WO2013166626A1

WO2013166626A1 - Dual-drive parallel sequential booster compressor

Info

Publication number: WO2013166626A1
Application number: PCT/CN2012/000713
Authority: WO
Inventors: 王航; 李永泰; 朱智富; 李延昭; 袁道军; 王艳霞; 宋丽华
Original assignee: Wang Hang; Li Yongtai; Zhu Zhifu; Li Yanzhao; Yuan Daojun; Wang Yanxia; Song Lihua
Priority date: 2012-05-07
Filing date: 2012-05-22
Publication date: 2013-11-14
Also published as: CN102720692A; CN102720692B; US20150063989A1

Abstract

A dual-drive parallel sequential booster compressor comprises a compressor housing (1). A compressor impeller (2) is installed inside the compressor housing (1). A compressor flow channel is provided inside the compressor housing (1). A compressor air inlet and a compressor air outlet in communication with the compressor flow channel respectively are provided on the compressor housing (1). An impeller air inlet flow channel is provided on the compressor impeller (2). The impeller air inlet flow channel is in communication with a compressor air inlet (3) and the compressor flow channel, respectively. The compressor is capable of mitigating surges of the compressor at a low-speed working condition of an engine and expanding an air inlet stream at a high-speed working condition of an engine, so as to improve the performance of the engine.

Description

Double drive parallel sequence booster compressor

Technical field:

The present invention relates to a supercharged compressor, and more particularly to a dual-pass compressor casing 1 single-pressure air compressor impeller double-drive parallel-stage supercharged compressor, which belongs to the field of internal combustion engine supercharging. Background technique:

The turbocharger uses the exhaust energy of the engine to drive the turbine to rotate, thereby driving the compressor impeller coaxial with the turbine to rotate at a high speed. The compressor pushes the compressed air into the engine cylinder, increasing the air volume of the engine, under pressure and The flow rate is promoted to make the combustion more fully, which increases the power of the engine and reduces the fuel consumption. At the same time, it reduces the emission of harmful substances and reduces the noise.

In recent years, with the increase in engine power, the supercharging technology needs to be continuously improved. This requires matching a higher performance turbocharger, thereby developing a high pressure ratio, high efficiency, and high reliability. Turbochargers with a wider range of available flow rates are essential for improving engine power and improving current engine power performance. However, the conventional turbocharger basically adopts a single impeller single-channel compressor, and the supercharger surge phenomenon is prone to occur in the low-speed working condition range of the engine, and the supercharger flow congestion phenomenon is likely to occur in the high-speed working condition range of the engine, and The higher pressure ratio, flow range and efficiency level that the turbocharger needs to meet cannot be effectively met. As a result, many engine applications are forced to use a two-stage turbocharging system. In terms of performance, the two-stage turbocharging system has many advantages, but compared to the conventional single-wheel turbocharger, the two-stage turbo is added. The pressure system is bulky and complicated in layout, and the design and production technology is difficult and the manufacturing cost is high. The two-stage turbocharging system is suitable for high-end engines and is difficult to promote.

Therefore, it is desirable to design a dual-drive parallel-stage supercharging compressor using a single-compressor impeller and a dual-compressor runner structure, which can effectively reduce the surge loss and large flow range of the small turbocharger flow range. Blocking effects and effectively widen the flow range of the turbocharger. Summary of the invention: The problem to be solved by the present invention is to provide a double-drive parallel-stage supercharging compressor which is mainly used for improving the surge effect of the small flow range of the turbocharger and the blocking effect of the large flow range, and effectively widening the flow range of the turbocharger. .

In order to solve the above problems, the present invention adopts the following technical solutions:

A double-drive parallel-stage supercharging compressor comprises a compressor casing, a compressor impeller is arranged in the compressor casing, a compressor flow passage is arranged in the compressor casing, and the compressor casing is respectively connected with the compressor flow passage Compressor inlet and compressor outlet;

The compressor impeller is provided with an impeller inlet flow passage, and the impeller inlet flow passage is respectively connected with the compressor inlet and the compressor flow passage.

The following is a further improvement of the above solution by the present invention:

The compressor flow path includes a compressor inner flow passage and a compressor outer side disposed on the compressor casing; the ratio of the inlet width of the compressor inner passage to the inlet width of the compressor outer passage is 0.;! ~ 10.

Further improvement: a compressor diffuser is arranged at the inlet of the flow passage in the compressor.

Further improvement: the compressor air outlet comprises a compressor inner runner air outlet communicating with the compressor inner flow passage and a compressor outer runner air outlet communicating with the compressor outer runner, the compressor inner runner outlet 1〜10。 The ratio of the width of the air outlet of the compressor is 0. 1~10.

Further improvement: the ratio of the ratio of the inlet width of the inner flow passage of the compressor to the inlet width of the outer passage of the compressor and the ratio of the width of the outlet of the flow passage in the compressor to the width of the outlet of the outer runner of the compressor Not the same.

Further improvement: the impeller inlet is provided with an impeller inlet and an impeller outlet, and the compressor impeller is provided with a partition plate arranged at a position between the impeller inlet and the impeller outlet, the partition plate The impeller inlet flow passage is divided into an impeller intake inner passage communicating with the inner passage of the compressor and an impeller intake outer passage communicating with the outer passage of the compressor.

Further improvement: a partition wall is disposed in the air inlet passage between the compressor impeller and the air inlet of the compressor, and the partition wall is arranged in an axial direction and is arranged in an entire circumference, the partition wall and the compressor impeller Pressure The air inlet passage between the air inlets of the machine is the inner passage of the compressor inlet and the outer passage of the compressor inlet.

Further improvement: The outer passage of the compressor inlet is located on the outward side of the passage in the inlet of the compressor.

Further improved: the inner passage of the compressor inlet is corresponding to and communicates with the inner flow passage of the impeller, and the outer passage of the inlet of the compressor corresponds to and communicates with the outer flow passage of the impeller.

Further improvement: the distance between the end of the partition wall near the inlet of the compressor and the inlet of the impeller is 60~: 100mrn, the partition wall is close to the end of the inlet of the compressor and the inlet of the compressor The distance is 5~20mm.

Further improvement: A plurality of fixed guide vanes are evenly arranged in the outer passage of the compressor inlet.

Further improvement: the outer passage of the inlet of the compressor, the outer flow passage of the impeller, and the outer flow passage of the compressor are normally open flow passages.

Further improvement: a butterfly valve is arranged in the inner passage of the compressor inlet near the inlet of the compressor, and a butterfly valve is matched with the passage in the inlet of the compressor, and the butterfly valve is provided with a valve shaft connected to one body The valve shaft drive is connected with a control mechanism, and the butterfly valve rotates around the valve shaft under the driving of the control mechanism, thereby opening or closing the inner passage of the compressor air inlet.

Another improvement:

An adjustable valve is arranged at a position of the inner flow passage of the compressor near the air outlet of the compressor inner passage, a valve shaft is connected to one end of the adjustable valve, a control mechanism is connected to the valve shaft drive, and the adjustable valve is in the control mechanism. The rotation of the valve shaft is driven to realize the opening or closing of the flow passage in the compressor.

Another improvement:

The ratio of the number of the number of the guide vanes to the number of the adjustable guide vanes is 0. 2 ~6. Further improvement: each adjustable guide vane is rotatably connected to a shifting fork, and the shifting fork is rotatably connected to the fork disc, and the shifting fork disc is rotated by the control mechanism to realize the rotation of the adjustable guide vane, thereby The opening or closing of the flow passage in the compressor is realized.

Another improvement:

The inner passage of the compressor inlet, the inner passage of the impeller inlet, and the inner passage of the compressor are normally open channels. Further improvement:

In the outer passage of the inlet of the compressor, near the impeller inlet, there are thousands of uniformly arranged adjustable guide vanes, and each of the adjustable guide vanes respectively corresponds to a gear matched with the gear, and the corresponding arrangement of the gears A gear disc, which can be rotated by the control mechanism to realize the rotation of the adjustable guide vane, thereby opening or closing the outer passage of the compressor inlet.

Another improvement:

An adjustable valve is arranged in the outer flow passage of the compressor near the air outlet of the compressor outer flow passage, and one end of the adjustable valve is connected with a valve shaft, and the wide door shaft drive is connected with a control mechanism, and the adjustable valve is driven by the control mechanism The lower shaft is rotated around the valve shaft to open or close the outer flow passage of the compressor.

The invention adopts the above technical solution. When the outer passage of the compressor inlet, the outer flow passage of the impeller, and the outer flow passage of the compressor are normally open flow passages, the butterfly valve scheme disposed near the inlet of the compressor is arranged! : The process of adjusting the valve arranged in the air outlet of the compressor inner passage and the working process of setting the adjustable flow vane on the compressor diffuser are the same.

When the engine is in the low speed range, the adjustable guide vane provided on the butterfly valve or the adjustable valve or the compressor diffuser is rotated by the control mechanism, and the inner passage of the compressor inlet or the compressor is The air outlet of the flow passage is closed, and the inner flow passage of the impeller and the inner passage of the compressor are connected with the inner passage of the air inlet of the compressor, so that the inner flow passage of the impeller and the inner flow passage of the compressor are also closed. When the fresh air is driven by the centrifugal force generated by the rotation of the compressor impeller, it is only sucked into the outer passage of the compressor inlet, and then enters the engine to participate in combustion through the impeller inlet flow passage and the compressor outer passage compression acceleration. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under the low speed condition of the engine can be effectively improved. When the engine is in the middle and high speed working conditions, the adjustable guide vane provided on the butterfly valve or the adjustable valve or the compressor diffuser rotates around the valve shaft under the control mechanism, and the inner passage of the compressor inlet Or open the air outlet of the compressor inner passage to open the inner flow passage of the impeller and the inner flow passage of the compressor at the same time. At this time, the fresh air is sucked into the compressor by the centrifugal force generated by the compressor impeller. The inner passage of the air port and the outer passage of the air inlet of the compressor. The fresh air entering the passage of the intake port of the compressor enters the engine and participates in combustion through the centrifugal force of the impeller in the inner flow passage of the impeller and the inner passage of the compressor. The fresh air entering the outer passage of the inlet of the compressor enters the engine and participates in combustion through the centrifugal force and the external flow passage of the impeller and the external flow passage of the compressor to accelerate the work. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.

When the inner passage of the compressor inlet, the inner passage of the impeller, and the inner passage of the compressor are normally open flow passages, the working process of the adjustable guide vane arrangement disposed near the inlet of the impeller is arranged close to the compression The working process of the adjustable valve solution at the air outlet of the machine is the same.

When the engine is in the low speed range, the adjustable guide vane and the adjustable valve are rotated by the control mechanism, and the outer passage of the compressor inlet or the outlet of the compressor outer passage is closed, due to the outer flow passage of the impeller. The outer flow passage of the compressor is connected to the outer passage of the inlet of the compressor, so the outer flow passage of the impeller and the outer flow passage of the compressor are also closed. At this time, the fresh air is only driven by the centrifugal force generated by the rotation of the compressor impeller. It is sucked into the inner passage of the compressor inlet, and then enters the engine to participate in combustion through the impeller intake inner passage and the compressor inner passage compression acceleration. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved.

When the engine is in the middle and high speed working conditions, the adjustable guide vane and the adjustable valve are rotated by the control mechanism, and the outer passage of the compressor inlet or the outlet of the compressor outer passage is opened, thereby injecting the impeller. The outer flow passage and the outer flow passage of the compressor are simultaneously opened. At this time, the fresh air is sucked into the inner passage of the compressor inlet and the outer passage of the compressor inlet by the centrifugal force generated by the compressor impeller. The fresh air entering the passage of the intake port of the compressor enters the engine and participates in combustion through the centrifugal force of the impeller in the inner flow passage of the impeller and the inner passage of the compressor. The fresh air entering the outer passage of the air inlet of the compressor enters the engine after the centrifugal force is applied to the external flow passage of the impeller and the external flow passage of the compressor to accelerate the work. The machine is involved in the burning. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.

In summary, the present invention adopts the above scheme, can effectively improve the compressor surge under the low speed condition of the engine, and can effectively widen the intake air flow under the high working condition of the engine and improve the engine performance. The compressor casing and the compressor impeller structure of the present invention have good inheritance and are easy to realize engineering quickly. The invention will be further described below in conjunction with the drawings and embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS:

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic view showing the structure of a double-drive parallel-stage supercharging compressor in the engine in a high-speed working condition range according to the first embodiment of the present invention;

2 is a schematic structural view of an air outlet of a double-drive parallel-stage supercharging compressor according to Embodiment 1 of the present invention; FIG. 3 is a schematic cross-sectional view of a compressor impeller of a dual-drive parallel-stage supercharged compressor according to Embodiment 1 of the present invention;

Figure 4 is a schematic view showing the structure of a compressor impeller of a double-drive parallel-stage supercharging compressor in Embodiment 1 of the present invention;

Figure 5 is a schematic view showing the structure of the double-drive parallel-stage supercharging compressor in the low-speed operating condition range of the engine in the first embodiment of the present invention;

6 is a schematic structural view of a double-drive parallel-stage supercharging compressor in Embodiment 2 of the present invention; and FIG. 7 is a schematic structural view of a compressor casing of a double-drive parallel-stage supercharging compressor in Embodiment 2 of the present invention;

8 is a schematic structural view of a double-drive parallel-stage supercharging compressor in Embodiment 3 of the present invention; and FIG. 9 is a perspective view of a dual-drive parallel-stage supercharging compressor in an engine and a high-speed working condition range according to Embodiment 3 of the present invention; Schematic;

Figure 10 is a compressor casing and control of a double-drive parallel-stage supercharging compressor in Embodiment 3 of the present invention. Schematic diagram of the structure of the institution;

Figure 11 is a schematic view showing the structure of a double-drive parallel-stage supercharging compressor in the low-speed operating range of the engine in Embodiment 3 of the present invention;

Figure 12 is a schematic view showing the structure of the double-drive parallel-stage supercharging compressor in the low-speed operating range of the engine in the fourth embodiment of the present invention.

Figure 13 is a structural schematic view showing the double-drive parallel-stage supercharging compressor of the embodiment 4 of the present invention in the middle and high operating conditions of the engine.

Figure 14 is a structural schematic view showing a compressor casing and a control mechanism of a double-drive parallel-stage supercharging compressor in Embodiment 5 of the present invention;

Figure 15 is a graph showing the characteristics of a compressor in Examples 1-5 of the present invention.

In the figure: 1-compressor casing; 2-compressor impeller; 3-compressor inlet; 4-compressor diffuser; 5-impeller inlet; 6-impeller outlet; 7-compressor inflow 8; compressor external flow passage; 9-compressor inner runner outlet; 10 - compressor outer runner outlet; 11-divider; 12-impeller inlet runner; 13- impeller inlet runner 14-partition wall; 15- compressor inner passage; 16-compressor inlet passage; 17-fixed guide vane; 18-butterfly valve; 19-wide shaft; 20-adjustable valve; - adjustable flow vane; 22-split; 23-fork disc; 24-gear; 25-gear disc.

detailed description:

Embodiment 1, as shown in FIG. 1 and FIG. 2, a double-drive parallel-stage supercharging compressor includes a compressor casing 1, a compressor impeller 2 is installed in the compressor casing 1, and a compressor gas is provided in the compressor casing 1 The compressor flow passage 1 is provided with a compressor air inlet 3 and a compressor air outlet respectively connected to the compressor flow passage, and the compressor impeller 2 is provided with an impeller intake flow passage, and the impeller intake flow passage respectively It is in communication with the compressor inlet 3 and the compressor flow passage. The compressor flow path includes a compressor inner flow passage 7 and a compressor outer flow passage 8 which are arranged side by side on the compressor casing 1; an intake port width W1 of the compressor inner flow passage 7 and an intake air of the compressor outer flow passage 8 1〜10。 The mouth width W2 ratio is 0. 1~10.

A compressor diffuser 4 is provided at the helium port of the flow passage 7 in the compressor.

The compressor air outlet includes a compressor inner runner air outlet 9 communicating with the compressor inner flow passage 7 and a compressor outer runner air outlet 10 communicating with the compressor outer runner 8, the compressor inner runner air outlet 1〜: 10。 The ratio of the ratio of the width W3 of the air outlet of the air outlet 10 is 0. 1~: 10.

The ratio of the ratio of the inlet width W1 of the compressor inner passage 7 to the inlet width W2 of the compressor outer passage 8 and the width W3 of the compressor inner passage outlet 9 and the compressor outer passage outlet 10 The ratio of the width W4 is not the same.

As shown in FIG. 3, the compressor impeller 2 is provided with an impeller inlet port 5 and an impeller outlet port 6, and the compressor impeller 2 is provided with a full circumference at a position between the impeller inlet port 5 and the impeller outlet port 6. a partitioning plate 11 that divides the impeller inlet flow passage into an impeller intake inner passage 12 that communicates with the compressor inner passage 7 and an impeller intake outer passage that communicates with the compressor outer passage 8 13.

As shown in Fig. 1, a partition wall 14 is disposed in the intake passage between the compressor impeller 2 and the compressor inlet 3, and the partition wall 14 is disposed in the axial direction and in the entire circumference.

The partition wall 14 spaces the inlet passage between the compressor impeller 2 and the compressor inlet 3 into a compressor inlet passage 15 and a compressor inlet passage 16.

The compressor inlet passage 16 is located circumferentially outward of the passage 15 in the compressor inlet.

The compressor inlet passage 15 is in communication with and communicates with the impeller intake passage 12, and the compressor inlet passage 16 corresponds to and communicates with the impeller intake passage 13 .

The compressor inlet passage 16 and the impeller inlet runner 13 and the compressor runner 8 are normally open passages.

The distance H between the end of the partition wall 14 adjacent to the intake port 3 of the compressor and the inlet port 5 of the impeller is 60 to 100 mm; the partition wall 14 is close to the end of the intake port 3 of the compressor and the intake of the compressor. The distance h between the ports 3 is 5 to 20 mm. A plurality of fixed guide vanes 17 are arranged uniformly in the outer passage 16 of the compressor inlet. The structural design is mainly used for fixing the connecting partition wall 14 and the compressor casing 1 on the one hand, and effectively guiding the compressor into the compressor on the other hand. The exhaust gas flow from the outer passage 16 of the intake port smoothly enters the outer flow passage 13 of the impeller.

A butterfly valve 18 is provided in the inner passage 15 of the compressor inlet near the compressor inlet 3 to cooperate with the compressor inner passage 15 of the compressor.

The butterfly valve 18 is provided with a valve shaft 19 connected to a body. The valve shaft 19 is connected with a control mechanism. The butterfly valve 18 rotates around the valve shaft 19 under the control mechanism, thereby pressing the compressor. The air inlet passage 15 is opened or closed.

As shown in FIG. 5, when the engine is in the low speed range, the butterfly valve 18 is rotated about the valve shaft 19 by the control mechanism, and the inner passage 15 of the compressor inlet is closed, due to the inner flow passage 12 of the impeller. The compressor inner flow passage 7 communicates with the compressor inner passage 15 so that the impeller intake inner passage 12 and the compressor inner passage 7 are also closed, and fresh air is rotated at the compressor impeller 2 at this time. The generated centrifugal force is only sucked into the outer passage 16 of the compressor inlet port, and then compressed and accelerated through the impeller intake outer flow passage 13 and the compressor outer flow passage 8 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing 1 is small, the compressor surge can be effectively improved under low engine speed conditions.

As shown in Fig. 1, when the engine is in the middle and high speed working conditions, the butterfly valve 18 is rotated around the valve shaft 19 by the control mechanism, and the inner passage 15 of the compressor inlet is opened, thereby injecting the inflow of the impeller. The channel 12 and the internal flow passage 7 of the compressor are simultaneously opened. At this time, the fresh air is sucked into the compressor inlet passage 15 and the compressor inlet passage 16 by the force generated by the compressor impeller 2. The fresh air entering the compressor inlet passage 15 is centrifugally driven by the impeller intake inner passage 12, and the compressor internal flow passage 7 is compressed and accelerated to enter the engine for combustion. The fresh air entering the outer passage 16 of the air inlet of the compressor is subjected to the centrifugal force by the outer flow passage of the impeller, and the outer flow passage 8 of the compressor is accelerated to work and then enters the engine to participate in the combustion. Since the cross-sectional area of the intake passage of the compressor casing 1 becomes large, the intake air amount in the engine under high working conditions is effectively widened, and the engine performance is improved.

Embodiment 2, as shown in FIG. 6 and FIG. 7, on the basis of Embodiment 1, the butterfly valve 18 disposed in the passage 15 of the compressor intake port is removed, and the flow passage 7 in the compressor is close to the compressor. 9 inner air outlets The position of the adjustable valve 20 is connected with a valve shaft 19, and the valve shaft 19 is driven and connected with a control mechanism, and is driven by the control mechanism to realize the opening of the flow passage 7 in the compressor. Or close.

The working process of this embodiment: As shown in Fig. 7, when the engine is in the low speed range, the adjustable valve 20 is closed under the control of the control mechanism (as shown by the solid line of the adjustable valve in the figure), at this time fresh air Driven by the centrifugal force generated by the rotation of the compressor impeller 2, it is only sucked into the compressor outer passage 16 and then compressed and accelerated by the impeller inlet flow passage 13 and the compressor outer passage 8 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved. And because the adjustable valve 20 is closed, the fresh air entering the engine intake pipe through the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the inner passage 7 of the compressor are blocked. In the middle and high speed working conditions of the engine, the adjustable valve 20 is opened under the driving of the control mechanism (as indicated by the dotted line of the adjustable valve in the figure), and the working process of this working condition is the same as that in the engine in the first embodiment. Working process under working conditions.

Embodiment 3, as shown in FIG. 8 and FIG. 9, on the basis of Embodiment 2, the adjustable valve 20 disposed near the air outlet 9 of the internal flow passage of the blower is removed, and the compressor diffuser 4 is disposed. 2〜6。 The ratio of the number of the number of the adjustable guide vanes 21 is 0. 2~6.

As shown in FIG. 10, each of the adjustable guide vanes 21 is rotatably connected to a shifting fork 22, and the shifting fork 22 is rotatably connected to the fork disc 23, and the shifting fork disc 23 is rotated by the control mechanism to realize The rotation of the flow vane 21 is adjusted to achieve opening or closing of the flow passage 7 in the compressor.

The control mechanism in this embodiment 3 is not limited to the shift fork control mechanism, and a control mechanism of any configuration can be selected.

The working process of this embodiment: As shown in FIG. 11, when the engine is in a low speed working condition range, the adjustable guide vane 21 is in a closed state under the driving of the control mechanism, and the centrifugal force generated by the fresh air rotating in the compressor impeller 2 at this time Under the driving, it is only sucked into the inner passage 15 of the compressor inlet and then compressed by the impeller internal flow passage 12 and the compressor inner flow passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake port of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved. Adjustable guide vane The sheet 21 is closed to block fresh air entering the engine intake pipe through the compressor inlet passage 16, the impeller inlet runner 13, and the compressor outlet runner 8. As shown in FIG. 9, when the engine is in the high-speed working condition range, the adjustable guide vane 21 is in an open state under the driving of the control mechanism, and the working process of this working condition is the same as the high-speed working condition in the engine in the first embodiment. The working process.

Embodiment 4, as shown in FIG. 12 and FIG. 13, different from the above-mentioned Embodiments 1, 2, and 3, the scheme is designed to design the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the internal flow of the compressor. Road 7 is a normally open flow path. On the basis of the first embodiment, the butterfly valve 18 disposed in the inner passage 15 of the compressor inlet is removed, and a plurality of uniformly arranged guide vanes are disposed in the outer passage 16 of the compressor inlet near the impeller port 5 of the impeller. 21, each of the adjustable guide vanes 21 respectively corresponds to a gear 24 matched thereto, and the gear 24 is correspondingly provided with a gear disc 25, and the gear disc 25 can be rotated by the control mechanism to achieve adjustable The rotation of the guide vanes 21 causes opening or closing of the outer passage 16 of the compressor inlet.

The control mechanism in this embodiment 4 is not limited to the gear control mechanism, and a control mechanism of any configuration can be selected.

The working process of this embodiment: As shown in FIG. 12, when the engine is in the low speed working condition range, the adjustable guide vane 21 is rotated by the control mechanism to close the compressor outer passage 16 due to the impeller intake. The outer flow passage 13 and the compressor outer flow passage 8 communicate with the compressor outer passage 16 so that the impeller intake outer flow passage 13 and the compressor outer flow passage 8 are also closed, and fresh air is rotated in the compressor impeller 2 at this time. The generated centrifugal force is only sucked into the inner passage 15 of the compressor intake port, and the shield is accelerated by the impeller intake inner passage 12 and the compressor inner passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under the low speed condition of the engine can be effectively improved.

As shown in FIG. 13, when the engine is in the middle and high-speed working condition range, the adjustable guide vane 21 is rotated by the control mechanism, and the compressor air inlet outer passage 16 is opened, thereby the impeller xenon outer flow passage 13, The compressor outer flow passage 8 is simultaneously opened, and at this time, the fresh air is sucked into the compressor inlet passage 15 and the compressor inlet passage 16 by the centrifugal force generated by the compressor impeller 2. The fresh air entering the passage 15 in the intake port of the compressor is compressed by the impeller intake inner passage 12 and the compressor inner passage 7 under the action of centrifugal force, and then enters the engine to participate in combustion. The fresh air entering the outer passage 16 of the compressor suffocating port is away Under the action of the heart force, the impeller intake outer flow passage 13 and the compressor outer flow passage 8 are compressed and accelerated to work, and then enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.

Embodiment 5 As shown in Fig. 14, the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the inner passage 7 of the compressor are designed as normally open passages. On the basis of the first embodiment, the butterfly valve 18 disposed in the inner passage 15 of the compressor inlet is removed, and an adjustable valve 20 is disposed in the outer flow passage 8 of the compressor near the outlet port 10 of the compressor outer flow passage. The adjustable valve 20 is connected to the control mechanism and driven by the control mechanism to open or close the compressor outer flow passage 8.

In the working process of the embodiment, when the engine is in a low speed working condition range, the adjustable valve 20 is in a closed state (shown by the solid line of the adjustable valve) driven by the control mechanism, and the fresh air is generated by the rotation of the compressor impeller 2 at this time. The centrifugal force is only sucked into the inner passage 15 of the compressor inlet and then compressed by the impeller inlet inner passage 12 and the compressor inner passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved. And because the adjustable valve 20 is closed, the fresh air entering the engine intake pipe through the compressor outer passage 16, the impeller intake outer passage 13 and the compressor outer passage 8 is blocked. In the middle and high speed working conditions of the engine, the adjustable valve 20 is opened under the driving of the control mechanism (as shown by the dotted line of the adjustable valve), and the working process of this working condition is the same as that in the engine in the fourth embodiment. Working process under working conditions. In the above embodiments 1-5, as shown in FIG. 15, when only one small compressor flow path is operated, it is a characteristic diagram of a small compressor (as shown by a broken line), when only one large compressor flow path works. When it is a characteristic map of a large compressor (as shown by the solid line), when designing two compressor runners to work together, the characteristic map of the compressor will cover the characteristic map of the compressor of the large and small flow passages. It can be clearly seen from the figure that after adopting this technical solution, the intake air flow range of the compressor is expanded, and two independent efficiency circles appear at the same time, which improves the performance of the compressor.

Claims

Rights request

1. A dual-drive parallel sequential boosting compressor, including a compressor casing (1). A compressor impeller (2) is installed in the compressor casing (1), and a compressor flow channel is provided in the compressor casing (1). , the compressor casing (1) is provided with a compressor air inlet (3) and a compressor air outlet that are respectively connected with the compressor flow channel;

Its characteristics are:

The compressor impeller (2) is provided with an impeller air inlet runner, and the impeller air inlet runner is connected to the compressor air inlet (3) and the compressor runner respectively.

2. The dual-drive parallel sequential boosting compressor according to claim 1, characterized in that - the compressor flow path includes a compressor inner flow path (7) and a compressor outer flow path arranged side by side on the compressor casing (1). channel (8); the ratio of the air inlet width (W1) of the compressor inner flow channel (7) to the air inlet width (W2) of the compressor outer flow channel (8) is 0.1~10.

3. The dual-drive parallel sequential boosting compressor according to claim 2, characterized in that: a compressor diffuser (4) is provided at the air inlet of the compressor inner flow channel (7).

4. The dual-drive parallel sequential boosting compressor according to claim 2 or 3, characterized in that: the compressor air outlet includes a compressor inner flow channel air outlet (7) connected with the compressor inner flow channel (7). 9) and the compressor outer flow channel air outlet (10) connected to the compressor outer flow channel (8), the width (W3) of the compressor inner flow channel air outlet (9) is consistent with the compressor outer flow channel air outlet (10) The ratio of width (W4) is 0.1~10.

5. The dual-drive parallel sequential boosting compressor according to claim 4, characterized in that: the air inlet width (W1) of the compressor inner flow channel (7) and the inlet width of the compressor outer flow channel (8) The ratio of the air port width (W2) is different from the ratio of the width (W3) of the compressor inner flow channel air outlet (7) to the width (W4) of the compressor outer flow channel air outlet (8).

6. The dual-drive parallel sequential boosting compressor according to claim 4, characterized in that: the compressor impeller (2) is provided with an impeller air inlet (5) and an impeller air outlet (6), and the compressor impeller (2) is provided with an impeller air inlet (5) and an impeller air outlet (6). 2) There is a partition plate (11) arranged all around, located between the impeller air inlet (5) and the impeller air outlet (6). The partition plate (11) divides the impeller air inlet flow path into an impeller air inlet inner flow path (12) connected to the compressor inner flow path (7) and an impeller air inlet outer flow path connected to the compressor outer flow path (8). Tao (13).

7. The dual-drive parallel sequential boosting compressor according to claim 6, characterized in that: a partition wall is provided in the air inlet channel between the compressor impeller (2) and the compressor air inlet (3). (14), the partition wall (14) is arranged along the axial direction and around the entire circumference, and the partition wall (14) connects the air inlet between the compressor impeller (2) and the compressor air inlet (3). The channel interval is the inner channel (15) of the compressor air inlet and the outer channel (16) of the compressor air inlet.

8. The dual-drive parallel sequential boosting compressor according to claim 7, characterized in that: the outer channel (16) of the compressor air inlet is located on the circumferential outside of the inner channel (15) of the compressor air inlet.

9. The dual-drive parallel sequential boosting compressor according to claim 8, characterized in that: the compressor air inlet inner channel (15) corresponds to and is connected with the impeller air inlet inner flow channel (12), so The compressor air inlet outer channel (16) corresponds to and is connected with the impeller air inlet outer flow channel (13).

10. The dual-drive parallel sequential boosting compressor according to claim 9, characterized in that: the end of the partition wall (14) close to the compressor air inlet (3) and the impeller air outlet (5) The distance (H) is 60~100mm, and the distance (h) between the end of the partition wall (14) close to the compressor air inlet (3) and the compressor air inlet (3) is 5~20mm.

1. The dual-drive parallel sequential supercharging compressor according to claim 10, characterized in that: there are several fixed guide vanes (17) evenly arranged in the outer channel (16) of the compressor air inlet.

12. The dual-drive parallel sequential boosting compressor according to claim 11, characterized in that: the compressor air inlet outer channel (16), the impeller air inlet outer flow channel (13), the compressor outer flow channel (8) It is a constantly open flow channel.

13. The dual-drive parallel sequential supercharging compressor according to claim 12, characterized in that: the inner channel (15) of the compressor air inlet is provided with a connection with the compressor inlet near the compressor air inlet (3). A butterfly valve (18) matching the inner channel (15) of the air port. The butterfly valve (18) is provided with a valve shaft (19) integrally connected with it. The valve shaft (19) is drivingly connected with a control mechanism. , the butterfly valve (18) controls Driven by the mechanism, it rotates around the valve shaft (19), thereby opening or closing the inner channel (15) of the compressor air inlet.

14. The dual-drive parallel sequential boosting compressor according to claim 12, characterized in that: the compressor inner flow channel (7) is provided with an adjustable position near the air outlet (9) of the compressor inner flow channel. Valve (20), one end of the adjustable valve (20) is connected to a valve shaft (19), the valve shaft (19) is drivingly connected with a control mechanism, and the adjustable valve (20) is driven by the control mechanism around the valve shaft (19). 19) Rotate to open or close the flow passage (7) in the compressor.

15. The dual-drive parallel sequential supercharging compressor according to claim 12, characterized in that: the compressor diffuser (4) is evenly provided with a number of adjustable annular-shaped diffusers near the impeller outlet (6). Guide vanes (21), the ratio of the number of fixed guide vanes (17) to the number of adjustable guide vanes (21) is 0.2~6.

16. The dual-drive parallel sequential boosting compressor according to claim 15, characterized in that: each of the adjustable guide vanes (21) is rotatably connected to a shift fork (22), and the shift fork (22) The fork plate (23) is rotated and connected. The fork plate (23) is driven by the control mechanism to rotate to realize the rotation of the adjustable guide vane (21), thereby opening or closing the flow channel (7) in the compressor. .

17. The dual-drive parallel sequential boosting compressor according to claim 10, characterized in that: the compressor air inlet inner channel (15), the impeller air inlet inner flow channel (12), the compressor inner flow channel ( 7) It is a normally open flow channel.

18. The dual-drive parallel sequential boosting compressor according to claim 17, characterized in that: a number of evenly arranged adjustable guides are provided in the outer passage (16) of the compressor air inlet near the impeller air outlet (5). Flow blades (21), each of the adjustable flow guide blades (21) corresponds to a matching gear (24), and the gear (24) is correspondingly provided with a gear plate (25). The gear plate (25) 25) It can be rotated under the driving of the control mechanism to realize the rotation of the adjustable guide vane (21), thereby realizing the external passage of the compressor air inlet.

(16) on or off.

19. The dual-drive parallel sequential boosting compressor according to claim 1, characterized in that: an adjustable valve (10) is provided in the compressor outer flow channel (8) close to the compressor outer flow channel air outlet (10). 20), One end of the adjustable valve (20) is connected to a valve shaft (19), and the valve shaft (19) is drivingly connected to a control mechanism. The adjustable valve (20) rotates around the valve shaft (19) driven by the control mechanism, thereby Realize the opening or closing of the outer flow channel (8) of the compressor.