JP2013199921A - Turbocharger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbocharger which is compact in size and can make compatible high torque and a high output, and a countermeasure of exhaust gas.SOLUTION: There is provided a twin turbine type turbocharger in which a compressor side is disposed at the center of a turbo side composed of a first turbine housing and a second turbine housing. The compressor includes: a symmetric compressor impeller composed of one compressor impeller 19 and the other compressor impeller 20; and a compressor housing which encapsulates the symmetric compressor impeller and includes one air chamber enclosing the air suction port of the one compressor impeller and the other air chamber enclosing the air suction port of the other compressor impeller, at the respective side faces of the compressor housing, and also includes an air inlet 4 communicating with the one air chamber and the other air chamber and a discharge outlet 5 for the air accelerated by the symmetric compressor impeller.

Description

  In the present invention, for the purpose of enhancing the torque and output of the engine, the turbine impeller is rotated using exhaust gas, and the compressor impeller disposed and fixed coaxially with the turbine impeller is rotated into the cylinder. It relates to a turbocharger that supercharges air.

  The conventional turbocharger has a small absolute exhaust gas amount and exhaust gas pressure enough to sufficiently rotate the turbine impeller in the turbine housing, particularly in the low and medium speed rotation region of the engine. To cope with this, we have dealt with by reducing the diameter and weight of turbine blades and compressor impellers.

Problems to be solved by the invention

However, when the diameter of the turbine impeller or compressor impeller is reduced, the output tends to reach a peak, for example, when the engine reaches a high speed rotation range, the exhaust gas hardly passes through the turbine impeller.
In recent years, there has been a tendency to adopt engines with a small displacement for improving fuel efficiency and measures against exhaust gas, but high torque and high output are also required for engines with a small displacement.

In view of the above-described requirements, the initial object was achieved by the twin turbine turbocharger proposed in the application number “Application No. 2011-2011135” by the same applicant as the present applicant.
The twin-turbine turbocharger according to the previous application is characterized by having two turbine housings for wrapping the turbine impeller with respect to one compressor housing for wrapping the compressor impeller, and further reducing the diameter of the turbine impeller. The exhaust gas after rotating the turbine impeller in the turbine housing is supplied to the other turbine housing, and the turbine impeller in the other turbine housing is rotated to increase the rotational lifting force of the compressor impeller fixed on the same axis. .

  However, in the twin turbine turbocharger, the diameter of the turbine impeller could be reduced, but the compressor impeller was combined with a compressor impeller having the same specifications as the conventional type.

In this application, by adopting a compressor impeller with a reduced diameter after securing the ability to suck in air and overpressure the air, the inertial force is reduced and the turbocharger response is increased. The objective is to provide a turbocharger that can improve engine response, achieve higher torque, higher output, and exhaust gas countermeasures.
Furthermore, the twin turbine turbocharger according to the previous application has two turbine housings that enclose the turbine impeller. However, after ensuring the turbocharging capacity of the turbine impeller, the turbine housing is a single unit and the entire turbocharger is compact. It aims to make it easier.

Means for solving the problem

In order to achieve the above object, a twin turbine turbocharger according to claim 1 is characterized in that one compressor impeller and the other compressor impeller are provided between both sides of a hub and a back plate portion radially formed from the hub central portion. Includes a symmetrical compressor impeller integrally configured back-to-back with the back plate interposed therebetween, and one compressor housing including the symmetrical compressor impeller and one air chamber surrounding the air inlet of the one compressor impeller The other air chamber surrounding the air suction port of the other compressor impeller is provided on a side surface of the other compressor housing, and further includes an air introduction port communicating with the one air chamber and the other air chamber. , Air discharge of pressurized air by the symmetric compressor impeller The compressor side comprising the compressor housings respectively provided with the first turbine impeller contains the first turbine housing provided with the exhaust gas introduction port and the exhaust gas discharge port, and the second turbine impeller contains the exhaust gas. It is arranged in the center of the turbo side constituted by a second turbine housing provided with an introduction port and an exhaust gas discharge port, respectively, and a rotation shaft is provided between the compressor housing and the first turbine housing and between the compressor housing and the second turbine housing. It is configured integrally through a first bearing housing and a second bearing housing to be supported, a symmetric compressor impeller is fixed at the center of the rotating shaft, and a first turbine impeller and a second turbine impeller are fixed at both ends of the rotating shaft. It is characterized by .

  In order to achieve the above object, a single turbine turbocharger according to claim 2 is characterized in that one compressor impeller and the other compressor impeller are disposed between both sides of a hub and a back plate portion radially formed from the hub central portion. Includes a symmetrical compressor impeller integrally configured back-to-back with the back plate interposed therebetween, and one compressor housing including the symmetrical compressor impeller and one air chamber surrounding the air inlet of the one compressor impeller The other air chamber surrounding the air suction port of the other compressor impeller is provided on a side surface of the other compressor housing, and further includes an air introduction port communicating with the one air chamber and the other air chamber. Air discharge of air pressurized by the symmetric compressor impeller A bearing housing that supports a rotating shaft is provided on the compressor side that is configured by a compressor housing provided with a port, and the turbo side that includes a turbine impeller and is provided with an exhaust gas introduction port and an exhaust gas discharge port. And a symmetric compressor impeller and a turbine impeller are fixed to both ends of the rotating shaft, respectively.

In order to achieve the above object, a symmetric turbine turbocharger according to claim 3 is provided with a turbine impeller between both sides of a hub and a back plate portion formed radially and circularly from the center of the hub. The other turbine impeller includes a symmetric turbine impeller integrally configured back-to-back with the back plate portion interposed therebetween, and the symmetric turbine impeller, and the inside of the turbine housing is surrounded by the outer periphery of the back plate portion of the symmetric turbine impeller. The inner peripheral surface of the turbine housing is formed in a shape that maintains a slight clearance from the outer periphery of the back plate portion so that the turbine housing is divided into one turbine housing and the other turbine housing as much as possible. Each turbine housing has a dedicated exhaust gas inlet, and the one turbine impeller A turbine configured such that one exhaust gas chamber surrounding the exhaust gas discharge port is provided on one side of the turbine housing and the other exhaust gas chamber surrounding the exhaust gas discharge port of the other turbine impeller is provided on the other side of the turbine housing. A first exhaust pipe is fixed to the exhaust gas introduction port of the one turbine housing, and a second exhaust pipe is fixed to the exhaust gas introduction port of the other turbine housing. A first series of through holes communicating the first exhaust pipe and the second exhaust pipe to the AA ′ portion where exhaust gas flowing in the exhaust pipe and the second exhaust pipe flows in the same direction; and the first series A first switching valve is provided for switching the through hole to an open state or a closed state, and a third exhaust pipe is fixed to one exhaust gas chamber that surrounds the exhaust gas discharge port of one turbine impeller. A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe to the BB ′ portion in which exhaust gas flowing through the third exhaust pipe and the second exhaust pipe flows in the same direction; The second switching valve for switching the second communication hole to the open state or the closed state is provided, and the turbo side configured by fixing the fourth exhaust pipe in the other exhaust gas chamber includes the first compressor impeller, and the air introduction port and The turbine housing is disposed in the center of the compressor side, which includes a first compressor housing provided with an air discharge port and a second compressor housing containing a second compressor impeller and provided with an air introduction port and an air discharge port, respectively. Between the first compressor housing and between the turbine housing and the second compressor housing, Together are integrally configured through the bearing housing, symmetric turbine impeller is fixed to the center the rotation axis, the first compressor impeller and the second single compressor impeller, characterized in that fixed to the rotating shaft at both ends.

  In order to achieve the above object, according to a fourth aspect of the present invention, there is provided a turbocharger comprising: one turbine impeller and the other turbine impeller between a hub and both side surfaces of a back plate portion formed radially and circularly from the hub central portion. Includes a symmetric turbine impeller integrally configured back-to-back with the back plate interposed therebetween, and the symmetric turbine impeller, and the turbine housing has one turbine housing by an outer periphery of the back plate portion of the symmetric turbine impeller. The inner surface of the turbine housing is shaped to maintain a slight gap with the outer periphery of the back plate portion, and the one turbine housing and the other turbine housing respectively. Is provided with a dedicated exhaust gas inlet, and the exhaust gas outlet of the one turbine impeller One of the surrounding exhaust gas chambers is provided on one side of the turbine housing, and the other exhaust gas chamber that surrounds the exhaust gas discharge port of the other turbine impeller is provided on the other side of the turbine housing. A first exhaust pipe is fixed to the exhaust gas inlet of the one turbine housing, and a second exhaust pipe is fixed to the exhaust gas inlet of the other turbine housing, and the first exhaust pipe and the second exhaust pipe A first through hole communicating with the first exhaust pipe and the second exhaust pipe and an open state of the first through hole in the AA ′ portion where the exhaust gas flowing through each pipe of the exhaust pipe flows in the same direction Alternatively, a first switching valve for switching to a closed state is provided, and a third exhaust pipe is fixed to one exhaust gas chamber surrounding the exhaust gas discharge port of one turbine impeller, A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe, and a state where the second communication hole is opened, in the BB ′ portion where the exhaust gas flowing in each pipe of the two exhaust pipes flows in the same direction Alternatively, a second switching valve for switching to the closed state is provided, and the turbo side is configured by fixing the fourth exhaust pipe in the other exhaust gas chamber, the hub, and both sides of the back plate portion radially formed from the hub central portion Between the planes, one compressor impeller and the other compressor impeller are integrally configured back-to-back with the back plate portion interposed therebetween, and the symmetrical compressor impeller is included, and the air of the one compressor impeller One air chamber surrounding the air inlet is provided on the side of one compressor housing, and the other air chamber surrounding the air inlet of the other compressor impeller A compressor provided on a side surface of the other compressor housing, and further provided with an air introduction port communicating with the one air chamber and the other air chamber, and an air discharge port for air pressurized by the symmetric compressor impeller A compressor side constituted by a housing is integrally formed through a bearing housing that supports a rotating shaft, and a symmetric compressor impeller and a symmetric turbine impeller are respectively fixed to both ends of the rotating shaft.

  In order to achieve the above object, according to a fifth aspect of the present invention, there is provided a turbocharger according to claim 5, wherein one turbine impeller and the other turbine impeller are disposed between both sides of a hub and a back plate portion formed radially and circularly from the hub central portion. Includes a symmetric turbine impeller integrally configured back-to-back with the back plate interposed therebetween, and the symmetric turbine impeller, and the turbine housing has one turbine housing by an outer periphery of the back plate portion of the symmetric turbine impeller. The inner surface of the turbine housing is shaped to maintain a slight gap with the outer periphery of the back plate portion, and the one turbine housing and the other turbine housing respectively. Is provided with a dedicated exhaust gas inlet, and the exhaust gas outlet of the one turbine impeller One of the surrounding exhaust gas chambers is provided on one side of the turbine housing, and the other exhaust gas chamber that surrounds the exhaust gas discharge port of the other turbine impeller is provided on the other side of the turbine housing. A first exhaust pipe is fixed to the exhaust gas inlet of the one turbine housing, and a second exhaust pipe is fixed to the exhaust gas inlet of the other turbine housing, and the first exhaust pipe and the second exhaust pipe A first through hole communicating with the first exhaust pipe and the second exhaust pipe and an open state of the first through hole in the AA ′ portion where the exhaust gas flowing through each pipe of the exhaust pipe flows in the same direction Alternatively, a first switching valve for switching to a closed state is provided, and a third exhaust pipe is fixed to one exhaust gas chamber surrounding the exhaust gas discharge port of one turbine impeller, A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe, and a state where the second communication hole is opened, in the BB ′ portion where the exhaust gas flowing in each pipe of the two exhaust pipes flows in the same direction Alternatively, a second switching valve for switching to a closed state is provided, and a turbo side configured by fixing the fourth exhaust pipe to the other exhaust gas chamber, a hub, and a back plate that is formed radially and circularly from the center of the hub A symmetric compressor impeller in which one compressor impeller and the other compressor impeller are integrally configured back to back with the back plate interposed therebetween, and the symmetric compressor impeller, Compressor housing so that the outer periphery of the back plate of the impeller divides the compressor housing into one compressor housing and the other compressor housing as much as possible. The inner peripheral surface is shaped to maintain a slight gap with the outer periphery of the back plate portion, and one air chamber surrounding the air suction port of the one compressor impeller is provided on one compressor housing side surface, and The other air chamber surrounding the air intake port of the other compressor impeller is provided on the side of the other compressor housing, and is further pressurized by the air discharge port of air pressurized by one compressor impeller and the other compressor impeller. A compressor housing having a dedicated air discharge port for air, and a first air introduction pipe fixed to the one air chamber side and a first intake pipe fixed to the air discharge port side The second air introduction pipe is fixed to the other air chamber side and the second air introduction pipe is Two intake pipes are fixed, the first intake pipe and the second air introduction pipe communicate with each other through a third intake pipe, and the first intake pipe is connected to a third communication hole through which the first intake pipe and the third intake pipe communicate. A third switching valve for opening and closing the communication between the pipe and the third intake pipe is provided, and the communication portion between the third intake pipe and the second air introduction pipe is provided between the third intake pipe and the other compressor impeller, or The compressor side, which is configured by providing a fourth switching valve for switching communication between the second air introduction pipe and the other compressor impeller, is integrated with a bearing housing that supports the rotating shaft, and is symmetrical at both ends of the rotating shaft. The compressor impeller and the symmetric turbine impeller are fixed respectively.

Effect of the invention

  Since the inventions according to claims 1 to 5 are configured as described above, the following effects can be obtained.

  The twin turbine turbocharger according to claim 1 of the present invention has one compressor impeller and the other compressor impeller on the turbo side and the exhaust system of the twin turbine turbocharger proposed in Japanese Patent Application No. 2011-201135. Combined with a symmetric compressor impeller constructed by

Therefore, when starting or at low speed, an exhaust passage is constructed in which exhaust gas discharged from all cylinders is supplied to the first turbine impeller enclosed by the first turbine housing, and the first turbine impeller is rotated. After that, the exhaust passage that supplies the exhaust gas that still has energy to the second turbine impeller enclosed by the second turbine housing is constructed, so the first turbine impeller that reduces the inertia force and reduces the diameter is The exhaust gas exhausted from all the cylinders is supplied to the second turbine housing, and the second turbine housing envelops the exhaust gas which still has energy after the first turbine impeller is rotated. By being supplied to the two-turbine impeller, the first turbine impeller and the second turbine impeller 12 are able to rotate and rise vigorously. In addition, the symmetrical compressor impeller composed of one compressor impeller arranged and fixed on the same rotating shaft and the other compressor impeller secures the ability to suck in air and accelerate the air with the inertial force. Since the reduction of the diameter and the reduction of the diameter are achieved, the symmetric compressor impeller rotates and rises vigorously, improving the engine response and enhancing the supercharging effect at the time of starting and low speed rotation.
Further, even in the high speed rotation region, the exhaust gas discharged from the engine is divided into two parts, and the two divided exhaust gases are supplied to the first turbine impeller 7 and the second turbine impeller 12, respectively. The exhaust gas passing through the impeller 7 and the second turbine impeller 12 flows without clogging, the first turbine impeller 7 and the second turbine impeller 12 rotate and rise vigorously, and are arranged and fixed on the same rotational axis. The compressor impeller 1 also rotates and rises vigorously, and the supercharging effect can be enhanced even in the high speed rotation range.

The symmetric compressor impeller is arranged back-to-back with one compressor impeller and the other compressor impeller sandwiching the back plate, and each turbine impeller on the turbo side is also placed in the opposite direction with the symmetric compressor impeller sandwiched between them. Therefore, especially at high rotation, the axial force due to the exhaust gas pressure applied to the rotating shaft and the sucked air pressure cancels each other, so that the rotating shaft is not biased in one direction, and the bearing of the rotating shaft -The load on the seal mechanism and the like is reduced, and the durability of the bearing and seal mechanism can be increased.
In addition, the space between the symmetric compressor impeller and the compressor housing or between each turbine impeller and the turbine housing can be narrowed to reduce the air and exhaust gas leaking from each space, thereby improving the turbocharger supercharging efficiency. Can do.

  Since the single turbine type turbocharger in the invention described in claim 2 employs the compressor side constituted by the symmetric compressor impeller and the compressor housing in the twin turbine turbocharger described in claim 1, the air in the compressor impeller is sucked. It is possible to reduce the inertia force and reduce the diameter of the symmetric compressor impeller while securing the capacity and the ability to accelerate air, improving the engine response and enhancing the supercharging effect.

  Further, compared with the twin turbine turbocharger, the single turbine turbocharger according to the invention of claim 2 is combined with a single turbo side configured by a turbine housing that encloses the turbine impeller. It is simple, can be made compact, can be manufactured at low cost, and can provide a turbocharger at low cost.

  The symmetric turbine turbocharger according to the invention of claim 3 employs a symmetric turbine impeller in which one turbine impeller and the other turbine impeller are arranged back-to-back with the back plate portion interposed therebetween on the turbo side. Compressor that can reduce the inertial force and reduce the diameter while ensuring the efficiency of gas introduction and exhaust gas discharge, and further comprises a compressor impeller and the compressor impeller on the compressor side, and an air suction part and a discharge part. Since it has two housings, the inertial force of the compressor impeller can be reduced and the diameter can be reduced. As a result, the response of the turbocharger can be improved, and the engine response, torque and output can be improved.

  In particular, the symmetrical turbine impeller employs an exhaust system in which an exhaust path in which one turbine impeller and the other turbine impeller in the symmetrical turbine impeller are arranged in series at the time of starting or at low speed rotation is used. All the exhaust gas discharged from the turbine impeller is supplied only to one turbine impeller, and then the exhaust gas after rotating one turbine impeller is supplied to the other turbine impeller. The engine can be rotated, and the supercharging can be increased even when starting or rotating at a low speed, and the engine response, torque and output can be improved.

  Furthermore, at the time of high speed rotation, an exhaust system in which an exhaust path in which one turbine impeller and the other turbine impeller are arranged in parallel is adopted, so that the exhaust gas discharged from the engine is separated from the one turbine impeller Since it is supplied to the other turbine impeller in two parts, it is possible to continue to vigorously rotate one turbine impeller and the other turbine impeller even during high-speed rotation when the exhaust gas amount and exhaust gas pressure are increased. Also, the compressor impeller on the same rotating shaft can also rotate and rise, and supercharging can be further increased.

  Compared to the conventional turbocharger that had to deal with the entire rotation range from one start to the low-speed rotation range and high-speed rotation by one turbine impeller, it consists of one turbine impeller and the other turbine impeller The symmetric turbine impeller thus made has a wide design freedom and can further enhance the supercharging effect.

In the symmetric turbine impeller, one turbine impeller and the other turbine impeller are arranged back to back with the back plate portion interposed therebetween, and both compressor impellers are also arranged back to back with the symmetric turbine impeller interposed therebetween. For this reason, especially at high rotations, the force in the axial direction due to the exhaust gas pressure applied to the rotating shaft and the air pressure due to the sucked air cancels each other, reducing the load on the bearing and seal mechanism of the rotating shaft, The durability of the bearing / seal mechanism can be increased.
Therefore, the clearance between the symmetric turbine impeller and the turbine housing or between each compressor impeller and the compressor housing can be narrowed, and the turbocharging efficiency of the turbocharger can be improved by reducing the air and exhaust gas leaking from each clearance. Can do.

  Furthermore, since one turbine housing and the other turbine housing are integrated, the position of the exhaust gas discharge port in one turbine housing is close to the position of the exhaust gas introduction port in the other turbine housing. The third exhaust pipe communicating between the two can be set short in the low and medium speed rotation range, and while maintaining the exhaust gas pressure, temperature, etc. discharged from one turbine housing, move to the other turbine housing side Can be supplied.

  The turbocharger according to the invention of claim 4 employs a symmetric compressor impeller in which one compressor impeller and the other compressor impeller are arranged back to back across the disk portion on the compressor side. Since the inertial force can be reduced and the diameter of the turbocharger can be reduced while ensuring the ability to accelerate air, and the turbo side has the same configuration as that of the turbo side in the symmetric turbine turbocharger according to the invention of claim 3. By combining a symmetric compressor impeller and a symmetric turbine impeller with a reduced diameter, the turbocharger response can be improved and the engine response can be improved. Furthermore, since the supercharging effect can be enhanced, the torque It is possible to improve the output.

Further, the compressor housing that encloses the symmetric compressor impeller with a reduced diameter and the turbine housing that encloses the symmetric turbine impeller can be reduced in size, and the turbocharger body can be made compact.
In addition, a symmetric compressor impeller and a symmetric turbine impeller are arranged and fixed at both ends of the rotating shaft supported by the bearing housing, so the above-described effects can be ensured and the turbocharger body can be made compact. The degree of freedom of design increases with respect to the arrangement position of the turbocharger body and the arrangement position of the engine body equipped with the turbocharger.

  The turbocharger according to the fifth aspect of the invention employs the same configuration as that of the turbo side of the symmetric turbine type turbocharger according to the third aspect of the invention on the turbo side, so that the same effect as described above can be obtained. Also, on the compressor side, the first exhaust pipe, the second exhaust pipe, the third exhaust pipe on the turbo side, the first series passage hole and the first switching valve, the second communication hole and the second switching valve, etc. Since the first intake pipe, the second intake pipe, the third intake pipe, and the third communication hole and the third switching valve, the fourth communication hole and the fourth switching valve, etc. corresponding to During low-speed rotation, an air intake path is formed in which one compressor impeller and the other compressor impeller are arranged in series, and the air accelerated by one compressor impeller is further transferred to the other compressor impeller. To accelerate the presser impeller 127, it is possible to increase the supercharging effect during the starting or low-speed rotation.

In addition, in each turbocharger described above, by increasing the supercharging effect, the temperature and combustion pressure at the time of combustion are increased, and the turbocharging effect is further enhanced by supplying exhaust gas with increased temperature and pressure to the turbo side. By repeating these operations, the efficiency of the engine can be increased.
And by attaching to a small engine, it is possible to reduce fuel consumption and reduce carbon dioxide without sacrificing high performance.

  The schematic structure explanatory drawing which shows the Example in the twin turbine type turbocharger which employ | adopted the compressor housing which encloses the symmetrical compressor impeller and the said symmetrical compressor impeller in this invention.   The schematic structure explanatory drawing which shows the Example which combined the twin turbine type turbocharger proposed in application [application] number Japanese Patent Application No. 2011-201135 and the exhaust system which divides | segments exhaust gas by the same person as this applicant.   An embodiment in which a symmetric compressor impeller according to the present invention and a twin-turbine turbocharger that employs a compressor housing containing the symmetric compressor impeller are combined with an exhaust path having another configuration that divides exhaust gas discharged from an engine into two parts. FIG.   An embodiment in which a symmetric compressor impeller according to the present invention and a twin-turbine turbocharger that employs a compressor housing containing the symmetric compressor impeller are combined with an exhaust path having another configuration that divides exhaust gas discharged from an engine into two parts. FIG.   A single turbine turbo combined with a symmetrical compressor impeller according to the present invention, a compressor housing containing the symmetrical compressor impeller, and a turbine housing including the turbine impeller and provided with an exhaust gas introduction port and an exhaust gas discharge port The schematic structure explanatory drawing which shows the example of the charger.   Symmetric turbine impeller according to the present invention, a turbine turbine that encloses the symmetric turbine impeller, and a compressor turbine that encloses the compressor impeller and two compressor housings that are provided with an air inlet and an air outlet are combined. The schematic structure explanatory drawing which shows the example of the charger.   FIG. 2 is a schematic diagram illustrating the configuration of a symmetric turbine impeller and a rotation shaft.   The schematic structure explanatory drawing showing the arrangement position of the third exhaust pipe which communicates with the exhaust gas introduction part in the other turbine housing.   A symmetric compressor impeller according to the present invention, a compressor housing containing the symmetric compressor impeller, a turbocharger constituted by the symmetric turbine impeller and a turbine housing containing the symmetric turbine impeller, and exhaust gas discharged from the engine. The schematic structure explanatory drawing which shows the Example which combined the exhaust route which divides | segments.   An intake passage combined with a symmetric compressor impeller and a compressor housing containing the symmetric compressor impeller according to the present invention, and an exhaust gas that divides the exhaust gas combined with the symmetric turbine impeller and the turbine housing containing the symmetric turbine impeller into two parts The schematic structure explanatory drawing which shows the Example of the turbocharger comprised by a path | route.

1, 41, 55, 57, 96, 121 Symmetric compressor impeller 2, 34, 54, 58, 97, 122 Compressor housing 3 Twin turbine turbocharger 4 Air inlet 5, 118, 134, 139 Air outlet 6, 79 First bearing housing 7, 39, 52, 147, First turbine impeller 8, 13, 73, 76 Exhaust gas inlet 9, 14, 74, 77 Exhaust gas outlet 10, 36, 49, 151 First turbine housing 11, 82 Second bearing housing 12, 40, 53 Second turbine impeller 15, 38, 51 Second turbine housing 16, 64, 101, 123 Rotating shaft 17, 65, 124 Hub 18, 66, 125 Back plate 19, 115, 126 One compressor impeller 20, 116, 127 The other compressor Suppin blades 21, 23, 117, 119, 131, 136 Air suction ports 22, 132 One air chamber 24, 137 The other air chamber 25, 35, 48, 86, 108 First exhaust pipes 26, 37, 50, 87, 106 Second exhaust pipes 27, 43, 88, 107 First through holes 28, 42, 89, 104 First switching valves 29, 46, 90, 111, 150 Third exhaust pipes 30, 45, 91, 110, 149 Second communication hole 31, 44, 92, 109, 148 Second switching valve 32, 61, 94, 155 Fourth exhaust pipe 33 Compressor impeller 47a, 47b, 47c, 47d, 47e, 47f Exhaust pipe 59 Turbine impeller 60, 69 , 99 Turbine housing 62 Symmetric turbine turbocharger 63, 98, 153 Symmetric turbine impeller 67, 113 -Bin impeller 68, 114 The other turbine impeller 70 The outer periphery 71, 112 of the back plate portion The one turbine housing 72, 106 The other turbine housing 75, 78 The exhaust gas chamber 80 The first compressor impeller 81 The first compressor housing 83 The second compressor impeller 84 Second compressor housing 85a, 85b Heat shield cylinders 95, 154 Bearing housing 100, 120 Turbocharger 102, 103 Outer side 128 One compressor housing 129 Other compressor housing 130 Partition plate 133 First air introduction pipe 135 First intake pipe 138 Second air introduction pipe 140 Second intake pipe 141 Fourth intake pipe 142 Third intake pipe 143 Third communication hole 144 Third switching valve 145 Fourth communication hole 146 Fourth switching valve

  FIG. 1 shows a compressor impeller 33 and a compressor housing 34 including the compressor impeller 33 in a twin turbine turbocharger [FIG. 2] proposed in the application [application] number Japanese Patent Application No. 2011-201135 by the same applicant as the present applicant. FIG. 2 is a schematic explanatory view of a twin turbine turbocharger 3 in which the compressor side constituted by the above is replaced with a compressor side constituted by a symmetric compressor impeller 1 and a compressor housing 2 containing the symmetric compressor impeller 1 according to the present invention. .

  The twin turbine turbocharger 3 incorporating the symmetric compressor impeller 1 and the compressor housing 2 containing the symmetric compressor impeller 1 according to the present invention includes the symmetric compressor impeller 1 and introduces air as shown in FIG. A compressor side constituted by a compressor housing 2 constituted by a port 4 and an air discharge port 5 includes a first turbine impeller 7, and includes a first turbine housing 10 provided with an exhaust gas introduction port 8 and an exhaust gas discharge port 9, respectively. The second turbine impeller 12 is included, and an exhaust gas inlet 13 and an exhaust gas outlet 14 are provided in the center of the turbo side constituted by the second turbine housing 15. Between turbine housings 10 and the compressor Sa housing 2 and is between second turbine housing 15 are integrally configured via a respective first bearing housing 6 and the second bearing housing 11 for supporting the rotary shaft 16.

The symmetric compressor impeller 1 is fixed at the center of the rotary shaft 16, the first turbine impeller 7 and the second turbine impeller 12 are fixed at both ends of the rotary shaft 16, and the rotary shaft 16 includes the first bearing housing 6 and the first shaft. The two-bearing housing 11 is supported by a bearing / seal mechanism, and oil is circulated from the outside to the bearing / seal mechanism to lubricate and cool each part.
In FIG. 1, the bearing / seal mechanism and the hydraulic path that circulates oil from the outside to lubricate and cool each part are saved.

The symmetric compressor impeller 1 includes one compressor impeller 19 and the other compressor impeller 20 between both sides of a hub 17 fixed to a rotary shaft 16 and a back plate portion 18 formed radially from the center of the hub 17. Are arranged back to back with the back plate portion 18 in between, and the hub 17, the back plate portion 18, one compressor impeller 19 and the other compressor impeller 20 are integrally formed.
Further, in the symmetric compressor impeller 1 in FIG. 1, in order to rectify the air accelerated by the symmetric compressor impeller 1, the back plate portion 18 is formed in a circular shape from the central portion of the hub, and the spine formed in a circular shape is also provided. An embodiment in which the outer diameter of the plate portion 18 is set larger than the outer diameters of the outer portions of one compressor impeller 19 and the other compressor impeller 20 is also conceivable.

One compressor impeller 19 and the other compressor impeller 20 in the symmetric compressor impeller 1 are formed symmetrically with the back plate portion 18 as a center plane, and the specifications such as the dimensions and blade shapes of both are unified. planned.
In addition, the one compressor impeller 19 and the other compressor impeller 20 are integrally formed with the hub 17 and the back plate portion 18, but there is a case where a phase difference is provided to alternately shift the positions of the blades of the both, It is conceivable that the positions of the blades are set to the same phase, but they are appropriately selected according to the corresponding engine or the like.
Further, a combination method in which the dimensions and shapes of one compressor impeller 19 and the other compressor impeller 20 are different is also conceivable.

As described above, since the symmetric compressor impeller has one compressor impeller 19 and the other compressor impeller 20, it is possible to reduce the diameter while securing the ability to suck air and accelerate air. The first turbine impeller 7 and the second turbine impeller 12 can be reduced in diameter because they are combined with two turbine housings containing the turbine impeller.
Since the inertia performance ratio that makes it difficult to accelerate the turbocharger is proportional to the fifth power of the impeller diameter, reducing the diameter of the compressor and turbine impellers can reduce the inertial force of the compressor and turbine impellers and improve the engine response. Improve.

  Further, the rotary shaft 16 is supported by two locations of the first bearing housing 6 and the second bearing housing 11 which are arranged with a certain distance between the compressor housing 2, and further, one compressor impeller 19 and the other The compressor impeller 20 is integrally formed back-to-back with the back plate 18 interposed therebetween, and the first turbine impeller 7 and the second turbine impeller 12 are also arranged so that the back faces face both sides of the symmetrical compressor impeller 1. Therefore, especially at high speeds, the axial force due to the exhaust gas pressure applied to the rotating shaft 16 and the pressure due to the sucked air cancels each other, reducing the load on the bearing and increasing the durability. The rotational accuracy of the shaft 16 is improved, and the symmetric compressor impeller 1 and the compressor housing 2, between the first turbine impeller 7 and the first turbine housing 10, between the second turbine impeller 12 and the second turbine housing 15, and by reducing air and exhaust gas leaking from each gap, the turbo Improve the supercharging efficiency.

As for the method of fixing the symmetric compressor impeller 1 to the rotating shaft 16, in this embodiment, the rotating shaft 16 is constituted by one rotating shaft 16a and the other rotating shaft 16b, and the one rotating shaft 16a The symmetric compressor impeller 1 is fixed to the rotating shaft 16 by providing a screw or a female screw on the other rotating shaft 16b and screwing between the one rotating shaft 16a and the other rotating shaft 16b. An assembly type in which the diameter of the rotating shaft portion on which the symmetric compressor impeller 1 is assembled is reduced in diameter is adopted.
Further, the first turbine impeller 7 and the second turbine impeller 12 are respectively joined to the end of the one rotating shaft 16a and the end of the other rotating shaft 16b in advance by brazing and shrink fitting.

  In the above-described method, the rotary shaft 16 is composed of one rotary shaft 16a and the other rotary shaft 16b. However, the rotary shaft is manufactured as a single unit, and the rotary shaft has a symmetric compressor impeller, a first turbine impeller, A method of fixing the two-turbine impeller with a screw or the like is also conceivable, and the present invention is not limited to the above method, and various modifications are made in the method of fixing the symmetric compressor impeller, the first turbine impeller, and the second turbine impeller to the rotating shaft. You can also do it.

In the compressor housing 2 containing the symmetrical compressor impeller 1, one air chamber 22 surrounding the air inlet 21 of the one compressor impeller 19 is provided on one side surface of the compressor housing 2, and the other compressor impeller is provided. The other air chamber 24 surrounding the 20 air suction ports 23 is provided on the other side surface of the compressor housing, and further, the air introduction port 4 communicating with the one air chamber 22 and the other air chamber 24, and the symmetrical compressor Air discharge ports 5 for air pressurized by the impeller 1 are provided.
Air sucked from the air inlet 4 flows into one air chamber 22 and the other air chamber 24 communicating with the air inlet 4, and further flows into one compressor impeller 19 and the other compressor impeller 20. It is accelerated and supercharged from the air discharge port 5 to the intake side of the engine.

  Various methods for dividing the compressor housing 2, the first turbine housing 10, the second turbine housing 15, etc. in the twin turbine turbocharger 3 can be considered, but the main points are both sides sandwiching the symmetric compressor impeller 1. In addition, the first turbine impeller 7 and the second turbine impeller 12 are arranged and fixed to the rotary shaft 16 at fixed positions, respectively, and further, the compressor housing 2, the first turbine housing 10, the second turbine housing 15, The first bearing housing 6, the second bearing housing 11 and the like are intended to be assembled.

In the present embodiment, as one embodiment, the compressor housing 2 has a two-split type comprising a compressor housing 2a and a compressor housing 2b, and one air chamber 22 is formed in the compressor housing 2a in advance, and the compressor housing 2b The other air chamber 24 is formed in advance.
Further, the first turbine housing 10 and the second turbine housing 15 adopt the same configuration as that of the turbo side of the conventional turbocharger, and the first turbine housing 10 is constituted by the first turbine housing 10 and the partition plate 10a. The second turbine housing 15 adopts a two-split type constituted by the first turbine housing 15 and the partition plate 15a.

  As an example of how to assemble the twin turbine turbocharger 3, first, the compressor housing 2a and the first bearing housing 6 in which the partition plate 10a constituting the first turbine housing 10 is previously assembled are fitted or bolted. In addition, the compressor housing 2b and the second bearing housing 11 in which the partition plate 15b constituting the second turbine housing 15 is incorporated in advance are fixed by fitting, bolts, or the like.

Next, the other rotating shaft 16b to which the second turbine impeller 12 is joined is inserted into the second bearing housing 11, and the symmetric compressor impeller 1 is fitted into the other rotating shaft 16b.
Then, the compressor housing 2a and the compressor housing 2b6 are fixed by fitting, bolts or the like, and further, one rotating shaft 16a to which the first turbine impeller 7 is joined is inserted into the second bearing housing 6 and screwed in. The male screw of the other rotary shaft 16b and the female screw of the one rotary shaft 16a are integrated and fixed.
Thereafter, the first turbine housing 10 is fixed to the first bearing housing 6 incorporating the partition plate 10a by fitting, bolts, or the like, and the second turbine housing 15 is fixed to the first bearing housing 6 incorporating the partition plate 10b. It is fixed by fitting or bolts.
The fixing method is not limited to the fixing method using the male screw and the female screw, and a fixing method by fitting is also conceivable. Further, the dividing of the compressor housing 2 is not limited to the dividing method employed in this embodiment, and various modifications are made. You can also.

  In FIG. 1, when the twin turbine turbocharger 3 and the in-line four-cylinder engine are combined, the exhaust gas discharged from the engine is divided into two exhaust pipes, a first exhaust pipe 25 and a second exhaust pipe 26. The first exhaust pipe 25 communicates and is fixed to the first turbine housing 10 in the twin turbine turbocharger 3, and the second exhaust pipe 26 communicates and is fixed to the second turbine housing 15. Yes.

  Further, in the embodiment of FIG. 1, a series arrangement engine and one twin turbine turbocharger 3 are combined, but for the V arrangement engine and the horizontally opposed arrangement engine including the series arrangement engine, Embodiments in which a plurality of twin-turbine turbochargers or a plurality of turbochargers described later are combined are also conceivable.

  Regarding the exhaust system, the same configuration as the exhaust system in the twin turbine turbocharger [FIG. 2] proposed in the application [application] number Japanese Patent Application No. 2011-201135 by the same applicant as the present applicant was adopted. explain.

  The first exhaust pipe 25 and the second exhaust pipe 26 are piped in parallel so that the exhaust gas flowing in the two exhaust pipes smoothly merges in the same direction at the time of merging. A first series of through holes 27 communicating with the first exhaust pipe 25 and the second exhaust pipe 26, and a first switching for switching the first series of through holes 27 to an open state or a closed state. A valve 28 was provided.

The first switching valve 27 and the first switching valve 28 for switching the first communication hole 27 to an open state or a closed state are as shown in FIG. 28 continues to stop at the position where the first through hole 27 is in an open state, thereby blocking communication between the second exhaust pipe 26 and the second turbine housing 15, and between the first exhaust pipe 25 and the second air pipe 26. Establish an exhaust path that allows communication.
Further, when the engine speed increases and a preset switching time is reached, the first switching valve 28 continues to stop at a position where the first through hole 27 is closed, and the first exhaust pipe 25 and the second trachea 26, the first exhaust pipe 25 continues to communicate with the first turbine housing 10, and the second exhaust pipe 26 establishes an exhaust path that communicates with the second turbine housing 15. To do.

Further, a third exhaust pipe 29 is fixed to the exhaust gas discharge port 9 in the first turbine housing 10, and the exhaust gas flowing through the third exhaust pipe 29 is passed through the second exhaust pipe 26. The second exhaust pipe 26 and the third exhaust pipe are piped in parallel with the second exhaust pipe 26 in the middle so as to flow in the same direction as the exhaust gas flowing through the pipe. A second communication hole 30 that communicates with the second communication hole 29 and a second switching valve 31 that switches the second communication hole 30 to an open state or a closed state are provided.
Further, the arrangement position of the second communication hole 30 and the second switching valve 31 is set on the downstream side of the exhaust gas from the arrangement position of the above-described first communication hole 27 and the first switching valve 28.

The second switching hole 31 and the second switching valve 31 for switching the second communication hole 30 to an open state or a closed state are set to the second switching valve 31 when starting or at low speed rotation as shown in FIG. By continuing to stop the second communication hole 30 at a position where the second communication hole 30 is in an open state, an exhaust path is established in which the second exhaust pipe 26 and the third exhaust pipe 29 communicate.
By communicating between the second exhaust pipe 26 and the third exhaust pipe 29, the exhaust gas after rotating the first turbine impeller 7 contained in the first turbine housing 10 is not released into the atmosphere, and the second turbine It is supplied to the second turbine impeller 12 in which the housing 15 is contained.
Also, when the engine speed increases and the preset switching time is reached, the second switching valve 31 continues to stop at the position where the second communication hole 30 is closed, and the second exhaust pipe 26 and the third exhaust pipe 29, the first exhaust pipe 25 continues to communicate with the first turbine housing 10, and the exhaust gas after rotating the first turbine impeller 7 included in the first turbine housing 10 is released into the atmosphere. In addition, an exhaust path in which the second exhaust pipe 26 communicates with the second turbine housing 15 is constructed, and the exhaust gas after rotating the second turbine impeller 12 is discharged from the fourth exhaust pipe 32 to the atmosphere. .

Next, the operation of the above-described twin turbine turbocharger 3 will be described.
In the description, an automobile equipped with an engine equipped with the twin turbine turbocharger will be described as an example.
With the above-described configuration, an exhaust passage is constructed in which exhaust gas discharged from all cylinders is supplied to the first turbine impeller 7 included in the first turbine housing 10 at the time of starting or during low-speed rotation. The first turbine impeller 7 having reduced inertia force is supplied with exhaust gas discharged from all the cylinders, and vigorously rotates and rises.

  Furthermore, since the second switching valve 31 is also opened and the second communication hole 30 is closed, an exhaust passage for communication between the third exhaust pipe 29 and the second turbine housing 15 is constructed. After the turbine impeller 7 is rotated, the exhaust gas still having energy is supplied to the second turbine impeller 12 included in the second turbine housing 15, and the first turbine impeller 7 and the second turbine impeller 12 rotate. The symmetric compressor impeller 1 that is arranged and fixed on the same rotation shaft and reduced in diameter also rises vigorously from the start to the low to medium speed rotation range. Increases supercharging effect, improves engine response and increases torque.

Further, when the engine speed increases and a preset switching time is reached, the first switching valve 28 causes the first series through hole 27 communicating between the first exhaust pipe 25 and the second exhaust pipe 26 to be closed. As a result, the communication between the first exhaust pipe 25 and the second exhaust pipe 26 is cut off, and the first exhaust pipe 25 is constructed with an exhaust gas path for continuously supplying exhaust gas to the first turbine housing 10. The second switching valve 31 closes the second communication hole 30 that communicates between the second exhaust pipe 26 and the third exhaust pipe 29, thereby blocking communication between the second exhaust pipe 26 and the third exhaust pipe 29. Therefore, the second exhaust pipe 26 has an exhaust gas path communicating with the second turbine housing 15 and starts supplying exhaust gas to the second turbine housing 15.
The exhaust gas after rotating the first turbine impeller 7 is discharged into the atmosphere from the third exhaust pipe 29, and the exhaust gas after rotating the second turbine impeller 12 is discharged from the fourth exhaust pipe 32. Released into the atmosphere.

  Therefore, even in the high-speed rotation region, the exhaust gas discharged from the engine is divided into two parts, and the divided exhaust gas is supplied to the first turbine impeller 7 and the second turbine impeller 12, respectively. Since the exhaust gas passing through each of the turbine impeller 12 and the second turbine impeller 12 flows without clogging, the first turbine impeller 7 and the second turbine impeller 12 rotate and rise vigorously, and are further arranged and fixed on the same rotating shaft. The compressor impeller 1 also rotates and rises vigorously, and the supercharging effect can be enhanced even in the high speed rotation range.

  Therefore, it is composed of the compressor impeller 33 in the twin-turbine turbocharger [FIG. 2] and the compressor housing 34 containing the compressor impeller 33 proposed in the application [application] number Japanese Patent Application No. 2011-201135 by the same applicant as the present applicant. The twin-turbine turbocharger 3 in which the compressor side is replaced with the compressor side constituted by the symmetric compressor impeller 1 and the compressor housing 2 containing the symmetric compressor impeller 1 in the present invention has a supercharging effect over the entire rotation range. The engine response, torque and output can be increased from low to medium speed to high speed.

  The above-described twin turbine turbocharger 3 is a compressor impeller 33 of the twin turbine turbocharger shown in FIG. 2 and its compressor impeller 33 proposed in the application [application] No. 2011-201135 by the same applicant as the present applicant. The compressor side constituted by the compressor housing 34 enclosing the compressor is replaced with the compressor side constituted by the symmetric compressor impeller 1 and the compressor housing 2 containing the symmetric compressor impeller 1 according to the present invention. Application [application] number The same effect as the case where the twin turbine type turbocharger and each exhaust system in Japanese Patent Application No. 2011-201135 are combined can be acquired.

  Further, in the twin turbine turbocharger proposed in the application [application] number Japanese Patent Application No. 2011-201135 including FIG. 3 and FIG. 4, the compressor impeller in the twin turbine turbocharger and the compressor including the compressor impeller are included. By replacing the compressor side composed of the housing with the compressor side composed of the symmetric compressor impeller having a reduced diameter according to the present invention and the compressor housing containing the symmetric compressor impeller, the supercharging effect can be achieved over the entire rotation range. The engine response, torque, and output can be increased from low to medium speed to high speed.

  For example, the twin turbine turbocharger of FIG. 3 is not provided with the first switching valve, the first series hole, the second switching valve, the second communication hole, the third exhaust pipe, etc. in FIG. The first exhaust pipe 35 continues to communicate with the first turbine housing 36, and the exhaust gas guided by the first exhaust pipe 35 continues to be supplied only to the first turbine impeller 39 included in the first turbine housing 36. In addition, the state where the second exhaust pipe 37 communicates with the second turbine housing 38 is continued, and the exhaust gas guided by the second exhaust pipe 37 is supplied only to the second turbine impeller 40 included in the second turbine housing 38. Keep doing.

Therefore, when the first turbine impeller 39 and the second turbine impeller 40 rotate vigorously, the symmetric compressor impeller 41 arranged and fixed on the same rotation shaft also vigorously rotates and accelerates the sucked air, Air with increased boost pressure can be supplied to the engine.
The first turbine impeller 39 and the second turbine impeller 40 having a reduced diameter compared to a turbocharger in which one turbine housing containing a conventional turbine impeller and one compressor housing containing a compressor impeller are combined. Since the inertial force is reduced, the symmetric compressor impeller 41 can enhance the supercharging effect and increase the engine response, torque, and output from the low to medium speed rotation range to the high speed rotation range.

Further, the twin turbine turbocharger shown in FIG. 4 is an embodiment in which a twin turbine turbocharger and a three-cylinder engine are combined. Like the embodiment shown in FIG. A hole 43, a second switching valve 44, a second communication hole 45, a third exhaust pipe 46, and the like are provided.
The exhaust system of the present embodiment is provided with two independent exhaust pipes 47a to 47f per cylinder, and a first exhaust pipe 48 in which any one of the exhaust pipes 47a, 47c, 47e in each cylinder is assembled is a first. The second exhaust pipe 50 in which one of the other exhaust pipes 47b, 47d, 47f in each cylinder is assembled is fixed in communication with the second turbine housing 51.

In this embodiment, even in a 4-cylinder or 6-cylinder type even-cylinder engine, and in a 3-cylinder or 5-cylinder type odd-cylinder engine as in the embodiment of FIG. The gas can be divided into two equal parts in all rotation regions.
At the time of starting or at low speed rotation, the first switching valve 42 is kept open by the first switching valve 42, and the communication between the second exhaust pipe 50 and the second turbine housing 51 is blocked.
Therefore, the exhaust gas discharged from all the cylinders is supplied to the first turbine impeller 52 contained in the first turbine housing 49, and further, the exhaust gas after rotating the first turbine impeller 52 is used as the second turbine impeller. By supplying the second turbine impeller 53 contained in the housing 51, the symmetric compressor impeller 55 with reduced inertial force contained in the compressor housing 54 can be vigorously rotated and the supercharging effect can be enhanced.

  Further, when the engine speed increases and a preset switching time is reached, the exhaust gas discharged from all the cylinders and divided into two equal parts is led to the first exhaust pipe 48 and the second exhaust pipe 50, respectively. The first exhaust pipe 48 continues to supply exhaust gas to the first turbine impeller 52 included in the first turbine housing 49, and the second exhaust pipe 50 exhausts to the second turbine impeller 53 included in the second turbine housing 51. Continue to supply gas.

  Therefore, the interval between the exhaust gases supplied to the first turbine impeller 52 and the second turbine impeller 53 is shortened by half compared to the case of the twin turbine turbocharger 3 in FIG. 1, and the first turbine impeller 52 and the second turbine impeller 52 are reduced. Exhaust gas can always be continuously supplied to the impeller 53 at narrow equal intervals, and the symmetrical compressor impeller 55 arranged and fixed on the same axis can be smoothly rotated and raised.

  Furthermore, since the exhaust gas pressure at the time of blowdown that is blown out at the same time as the exhaust valve is opened is divided into two by the two exhaust pipes, the exhaust gas pressure applied to the first turbine impeller 52 and the second turbine impeller 53 is also two. It is possible to reduce by dividing, and it is possible to reduce the strength of the turbine impeller body, and it is possible to further reduce the weight of each turbine impeller.

  The symmetric compressor impeller 55 and the compressor housing 54 enclosing the symmetric compressor impeller 55 are replaced and combined with the reduced-diameter symmetric compressor impeller and the compressor housing enclosing the symmetric compressor impeller in the present invention. As a result, the symmetric compressor impeller with reduced inertial force can increase the rotation speed, increase the supercharging effect, and increase the engine response, torque and output from the low to medium speed range to the high speed range.

  Further, like the compressor side in FIG. 1, as in the embodiment of FIG. 5, the compressor side constituted by the symmetric compressor impeller 57 having a reduced diameter and the compressor housing 58 containing the symmetric compressor impeller 57, A conventional turbine impeller 59 and a turbo side composed of a turbine housing 60 containing the turbine impeller 59 are combined through a bearing housing that supports a shaft, and a symmetric compressor impeller 57 is screwed to one end of the rotating shaft. An embodiment of a single turbine turbocharger in which a turbine impeller 59 is joined to the other end of the rotating shaft is also conceivable.

  Compared to the twin turbine turbocharger described above, the single turbine turbocharger is combined with a turbine housing that contains a turbine impeller, so the structure of the turbocharger body is simple and compact, and it is manufactured. Cost can be finished at low cost.

  Further, in the above-described twin turbine turbocharger 3, as shown in FIG. 1, the compressor housing containing the symmetric compressor impeller is arranged in the center, and the first turbine housing and the second turbine housing are arranged on both sides of the compressor housing, The turbine impellers contained in both turbine housings rotate with exhaust gas exhausted from the engine, thereby rotating the symmetric compressor impeller and sucking air in the air to accelerate and boost the boost pressure. As shown in FIG. 6, a symmetric turbine turbocharger that adopts the same structure as the compressor side described above on the turbo side is also conceivable.

FIG. 6 shows an embodiment thereof. A symmetric turbine impeller 63 in a symmetric turbine turbocharger 62 includes a hub 65 supported by a rotating shaft 64 and a back plate portion that is formed radially and circularly from the central portion of the hub 65. 66, one turbine impeller 67 and the other turbine impeller 68 are arranged back to back with the back plate portion 66 in between, and the hub 65, the back plate portion 66, one turbine impeller 67, the other Each part of the turbine impeller 68 is integrally configured.
The back plate portion 66 has a role of dividing the inside of the turbine housing 69 into two as much as possible, and is formed radially and circularly from the central portion of the hub 65.
The basic configuration of the symmetric turbine impeller 63 is the same as that of the symmetric compressor impeller described above, but the turbine impeller and the compressor impeller have different roles, and therefore the shape and size of each blade are as follows. Of course, it is set to the shape, dimension, etc. adapted to the role.

  The turbine housing 69 containing the symmetric turbine impeller 63 is separated by the outer periphery 70 of the circular back plate 66 in the symmetric turbine impeller 63 and the inner peripheral surface of the turbine housing 69 facing the outer periphery 70. The outer periphery 70 of the back plate 66 and the outer periphery 70 are relatively separated from each other so as to be divided into a turbine housing 71 containing the turbine impeller 67 and the other turbine housing 72 containing the other turbine impeller 68 as much as possible. The turbine housing 69 is formed in a shape that maintains a slight gap between the inner peripheral surfaces.

  The slight gap described above is created by the outer periphery 70 of the back plate portion 66 and the inner peripheral surface of the turbine housing 69 facing the outer periphery 70. However, in order to reduce the diameter and weight of the entire symmetric turbine impeller 63, When the outer periphery 70 of the back plate portion 66 having a shape is reduced in diameter as much as possible, the turbine housing 69 is opposed to the outer periphery 70, and the turbine housing 69 is divided into one turbine housing 71 and the other turbine housing 72. In the case where the partition portion to be divided is required and the inside of the turbine housing 69 is divided into two turbine housings 71 and 72 by the outer periphery 70 of the circular back plate portion 66, a symmetric turbine impeller is provided. It is necessary to sacrifice the size and weight of the entire 63 to some extent. The same applies to other embodiments.

Further, the one turbine housing 71 divided into two is provided with an exhaust gas introduction port 73, and an exhaust gas chamber 75 surrounding the exhaust gas discharge port 74 of the one turbine impeller 67 is provided on the side surface. The other turbine housing 72 is provided with an exhaust gas introduction port 76, and an exhaust gas chamber 78 surrounding the exhaust gas discharge port 77 of the other turbine impeller 68 is provided on the side surface.
A third exhaust pipe 90, which will be described later, is connected and fixed to the exhaust gas chamber 75, and a fourth exhaust pipe 61 is connected and fixed to the exhaust gas chamber 78.

  A turbo side constituted by the above-described symmetrical turbine impeller 63 and the turbine housing 69 containing the symmetrical turbine impeller 63 is disposed in the center, and a first bearing housing 79 is provided on one side of the turbine housing 69 via a first bearing housing 79. A first compressor housing 81 that includes one compressor impeller 80 and is provided with an air inlet and an air outlet is disposed and coupled, and a second bearing housing 82 is provided on the other side of the turbine housing 69. A second compressor housing 84 including a second compressor impeller 83 and provided with an air inlet and an air outlet is disposed and coupled, and the above-mentioned parts are integrated to form a symmetric turbine turbocharger 62. Is configured.

  The symmetric turbine impeller 63 and the first compressor impeller 80 and the second compressor impeller 83 located on both sides of the symmetric turbine impeller 63 are arranged at respective fixed positions on the rotary shaft 64 after assembly, The rotary shaft 64 is supported by a bearing / seal mechanism in the first bearing housing 79 and the second bearing housing 82.

  The compressor side constituted by the symmetric compressor impeller 1 and the compressor housing 2 in FIG. 1 is for the purpose of sucking and accelerating air in the atmosphere, and therefore compared with the turbo side constituted by the turbine impeller and the turbine housing. The main body temperature is low, and the rotating shaft 16 joined to the symmetric compressor impeller 1 is kept at a low temperature. However, in FIG. 6, the symmetric turbine impeller 63 that rotates with exhaust gas exhausted from the engine, The turbine housing 69 that encloses the symmetric turbine impeller 63 and the rotating shaft 64 that is exposed in the high-temperature exhaust gas must be made of a material having excellent heat resistance.

Therefore, in order to prevent the rotary shaft 64 from being directly exposed to the exhaust gas, the central portion of one turbine housing 71 in the exhaust gas chamber 75 and the central portion of the other turbine housing 72 in the exhaust gas chamber 76 are This was dealt with by providing a heat shield cylinder 85a and a heat shield cylinder 85b each formed in a conical shape having a hollow hole through which the rotary shaft 64 passes. The heat shield cylinder 85a and the heat shield cylinder 85b also serve to guide exhaust gas to the exhaust pipe side.
An embodiment in which each heat shield cylinder 85a and heat shield cylinder 85b formed in a conical shape is formed of a metal plate having excellent heat resistance and fixed to the exhaust gas chamber 75 and the exhaust gas chamber 76 side is also conceivable.
Further, the heat shield cylinder 85a and the heat shield cylinder 85b and the rotary shaft 64 are not in direct contact with each other.

Furthermore, a method of manufacturing a rotating shaft with a metal having excellent heat resistance and joining with a turbine rotor made of metal or ceramic is also conceivable.
As shown in FIG. 7, the symmetrical turbine impeller 63 and the portion 64 a and the portion 64 b of the rotating shaft 64 exposed in the exhaust gas are integrally manufactured from a ceramic material that can cope with the exhaust gas heat. A symmetrical turbine impeller and a rotating shaft in which the part 64c and the part 64d that are not exposed inside are made of metal and joined together are also conceivable.

  The turbine housing 69, the first compressor housing 81, the second compressor housing 84, and the like in the symmetric turbine turbocharger 62 may be divided in various ways. The twin turbine type described in the embodiment of FIG. The turbocharger 3 may be assembled using the same dividing method as the compressor housing 2, the first turbine housing 10, the second turbine housing 15, or the like, or the same method as the conventional turbocharger.

The twin turbine turbocharger 62 is fixed to a first exhaust pipe 86 and a second exhaust pipe 87 that divide the exhaust gas discharged from the engine into two equal parts, and the first exhaust pipe 86 is connected to one turbine housing. The second exhaust pipe 87 is fixed in communication with the exhaust gas chamber 78 in the other turbine housing 72.
Further, the first exhaust pipe 86 and the second exhaust pipe 87 have a portion that is piped in parallel so that the exhaust gas flowing in both exhaust pipes flows in the same direction. A first series of through-holes 88 communicating with one exhaust pipe 86 and the second exhaust pipe 87, and a first switching valve 89 for switching the first series of through-holes 88 to an open state or a closed state are provided.
In addition, the first exhaust pipe 86 and the second exhaust pipe 87 are formed by connecting both exhaust pipes in parallel in a planar shape in the drawing. However, the embodiment is not limited to this, and the first exhaust pipe 86 and the second exhaust pipe 87 are rotated around the vertical direction in the drawing. Piping is also possible.

The first switching valve 89 and the first switching valve 89 for switching the first communication hole 88 to an open state or a closed state are configured so that the first switching valve 89 is in the first series at the time of starting or during low-speed rotation. The through-hole 88 continues to stop at a position where it is open, the communication between the second exhaust pipe 87 and the other turbine housing 72 is shut off, and the first exhaust pipe 86 and the second exhaust pipe 87 are kept in communication.
Further, when the engine speed increases and a preset switching time is reached, the first switching valve 89 continues to stop at a position where the first through hole 88 is closed, and the first exhaust pipe 86 and the second exhaust pipe 86 are stopped. The communication between the pipes 87 is cut off, the first exhaust pipe 86 keeps communicating with one turbine housing 71, and the second exhaust pipe 87 communicates with the other turbine housing 72.

Further, a third exhaust pipe 90 is fixed to the exhaust gas chamber 75 in one turbine housing 71.
The third exhaust pipe 90 is piped in parallel with the second exhaust pipe 87 in the middle so that the exhaust gas flowing in the third exhaust pipe 90 flows in the same direction as the exhaust gas flowing in the second exhaust pipe 87. The second communication hole 91 communicating between the second exhaust pipe 87 and the third exhaust pipe 90 and the second communication hole 91 in an open state or a closed state are connected to the BB ′ portion piped in parallel. A second switching valve 92 for switching is provided.
The positions of the second communication hole 91 and the second switching valve 92 are set on the downstream side of the positions of the first communication hole 88 and the first switching valve 89.

In FIG. 6, the second exhaust pipe 87 and the third exhaust pipe 90 are piped in parallel, but the second communication hole 91 and the second switching valve 92 are formed in the BB ′ portion piped in parallel. Therefore, the second exhaust pipe 87 and the third exhaust pipe 90 are illustrated in parallel on the left and right for the sake of explanation.
Therefore, the present invention is not limited to this, and in the implementation, as shown in FIG. 8, the exhaust gas chamber 78 surrounding the exhaust gas discharge port 77 of the other turbine impeller 68 and the second compressor housing 84 are avoided, and the third exhaust pipe 90 is provided. By piping the third exhaust pipe 90 in parallel with the second exhaust pipe 87 on the side surface where the exhaust gas chamber 78 and the second compressor housing 84 can be displaced so as to have a shape close to a straight line, The exhaust gas guided to the third exhaust pipe 90 can be smoothly poured into the exhaust gas guided by the second exhaust pipe 87.
The same applies to other embodiments.

The second switching hole 92 and the second switching valve 92 for switching the second communication hole 91 to an open state or a closed state are opened when the vehicle is started or rotated at a low speed. The second exhaust pipe 87 and the third exhaust pipe 90 are communicated with each other while continuing to stop at the position where the state is reached.
When the second exhaust pipe 87 and the third exhaust pipe 90 communicate with each other, the other turbine housing 72 contains the exhaust gas after rotating one turbine impeller 67 contained in one turbine housing 71. The turbine impeller 68 is supplied.

Further, when the engine speed increases and the preset switching timing is reached, the second switching valve 92 continues to stop at the position where the second communication hole 91 is closed, and the second exhaust pipe 87 and the third exhaust pipe Block communication between 90.
By blocking communication between the second exhaust pipe 87 and the third exhaust pipe 90, the first exhaust pipe 86 communicates with one turbine housing 71 to rotate one turbine impeller 67, and the second exhaust pipe 87. However, the other turbine impeller 68 is rotated in communication with the other turbine housing 72.

  With the above configuration, when starting or rotating at a low speed, the exhaust gas guided by the second exhaust pipe 87 flows into the exhaust gas guided by the first exhaust pipe 86, and all exhaust gas discharged from the engine is exhausted from the first exhaust pipe. It is supplied from the 86 side to one turbine impeller 67 in which one turbine housing 71 is contained.

  Further, after flowing into one turbine housing 71 and rotating one turbine impeller 67, the exhaust gas still having exhaust gas energy is converted into exhaust gas guided from the third exhaust pipe 90 to the second exhaust pipe 87. The other turbine impeller 68 contained in the other turbine housing 72 is rotated.

  Therefore, by rotating one turbine impeller 67 and then flowing into the other turbine housing 77 and rotating the other turbine impeller 68, the symmetric turbine impeller 63 rotates vigorously, and at the same time, the first compressor housing The air sucked by 82 is accelerated by the first compressor impeller 81 and supercharged to the engine side, and the air sucked by the second compressor housing 85 is accelerated by the second compressor impeller 84 and supercharged to the engine side.

  Further, when the engine speed increases and a preset switching time is reached, the first switching valve 89 continues to stop at a position where the first through hole 88 is closed, and the first exhaust pipe 86 continues. The exhaust gas continues to be supplied to one turbine housing 71 to rotate one turbine impeller 67, and the second switching valve 92 also stops at the position where the second communication hole 91 is closed. The exhaust pipe 87 communicates with the other turbine housing 72 and supplies exhaust gas to rotate the other turbine impeller 68.

Therefore, the exhaust gas guided to the first exhaust pipe 86 continues to be supplied to one turbine impeller 67 included in one turbine housing 71, and the exhaust gas guided to the second exhaust pipe 87 is The symmetric turbine impeller 63 rotates vigorously while continuing to be supplied to the other turbine impeller 68 contained in the other turbine housing 72.
Furthermore, the first compressor impeller 80 included in the first compressor housing 81 and the second compressor impeller 83 included in the second compressor housing 84 also rotate vigorously, and the first compressor housing 81 and the second compressor housing 84 Air sucked from the air inlet is accelerated and supercharged from each air outlet to the engine side.

  In the first switching valve 89 and the second switching valve 92 described above, when the engine speed increases and the preset switching timing is reached, the first switching valve 89 closes the first through hole 88. The second exhaust pipe 87 and the other turbine housing 72 are communicated with each other, the second switching valve 92 continues to stop at the position where the second communication hole 91 is closed, and one turbine housing 71 The exhaust gas discharged from the air was released to the atmosphere side. However, when the first communication hole 88 and the second communication hole 91 were closed at the same time, the engine speed was changed depending on the rotational speed at the time of switching. There may be a case where the rotation does not rise smoothly.

  Therefore, in order to cope with the case where the engine rotation does not rise smoothly, the shape and dimensions of each part including one turbine impeller 67, the other turbine impeller 68, the first compressor impeller 80, the second compressor impeller 83, etc. Further, optimization of the valve opening / closing timing of the first switching valve 89 and the second switching valve 92, and further, the valve closing timing of the second switching valve 92 is delayed with respect to the valve closing timing of the first switching valve 89, etc. It is necessary to make appropriate decisions based on design and experiments.

For example, when the first communication hole 88 and the second communication hole 91 are closed at the same time, it is conceivable that a drop in the supercharging amount to the engine side occurs depending on the rotational speed at the time of switching.
As one countermeasure, the valve closing timing of the second switching valve 92 is delayed with respect to the valve closing timing of the first switching valve 89, and the exhaust gas is continuously supplied to the other turbine impeller 68 included in the other turbine housing 72. Thus, a method of smoothly rotating and raising the symmetric turbine impeller 63 can be considered.
Further, a method of adjusting the ratio of the amount of exhaust gas supplied to the other turbine impeller 68 contained in the other turbine housing 72 and the amount of exhaust gas discharged to the atmosphere side by the valve opening degree of the second switching valve 92 is also conceivable. These are also determined as appropriate based on actual design and experiments.

  The first switching valve 89 and the second switching valve 92 are driven in conjunction with the negative pressure in the intake pipe, the solenoid, the driving force of the motor or stepping motor, etc., corresponding to the engine speed. In addition, as described above, a mechanism for adjusting the valve opening degree of the second switching valve 92 may be provided.

A turbocharger other than the above is also conceivable. As shown in FIG. 9, a bearing housing 95 that supports the rotating shaft 101 is arranged at the center, and a turbine housing that includes a symmetrical turbine impeller 98 in one of the bearing housings 95. A turbocharger 100 having an integrated configuration in which a turbo side constituted by 99 and a compressor side constituted by a compressor housing 97 containing a symmetric compressor impeller 96 is arranged on the other side of the bearing housing 95 is also conceivable.
In the turbocharger 100, the compressor side constituted by the symmetric compressor impeller 1 in FIG. 1 described above and the compressor housing 2 containing the symmetric compressor impeller 1, the symmetric turbine impeller 63 in FIG. A turbo side constituted by a turbine housing 69 containing a symmetric turbine impeller 63 is combined.

  A turbine impeller 98 is joined to one end of the rotating shaft 101, and a symmetric compressor impeller 96 is screwed to the other end of the rotating shaft 101, and the rotating shaft 101 is supported by a bearing / seal mechanism in the bearing housing 95. Further, the bearing / seal mechanism is lubricated and cooled by circulating oil from the outside.

  The symmetric turbine impeller 98 and the rotary shaft 101 are joined and integrated. In the portion 101a of the rotary shaft 101, the heat shield cylinder 85a and the shield in the embodiment of FIG. As in the case of the heat cylinder 85b, a hollow conical shape was formed so as to cover the rotating shaft portion 101a.

  In the turbocharger 100 of FIG. 9, the symmetric compressor impeller 96 and the symmetric turbine impeller 98 are respectively disposed and fixed at both ends of the rotating shaft 101, so that the outer surface 102 in the compressor housing 97 and the outer surface 103 in the turbine housing 99 are Each is blocked.

In FIG. 9, the bearing housing 95 that supports the rotating shaft 101 is arranged in the center. However, a bearing housing is added to the dotted line portion on the outer surface 102 of the symmetric compressor impeller 96 in FIG. It is conceivable to extend the rotating shaft and support it with an additional bearing housing. By supporting the rotating shaft at two locations, the rotational accuracy of the rotating shaft can be improved and stable rotational accuracy can be maintained.
The outer surface 102 of the symmetric compressor impeller 96 is lower in temperature than the outer surface 103 of the turbine housing 99 containing the symmetric turbine impeller 98, and the bearing / seal mechanism is easy to lubricate and cool, and rotates stably. The shaft can be supported.

  The compressor side constituted by the symmetric compressor impeller 96 and the compressor housing 97 containing the symmetric compressor impeller 96 includes the symmetric compressor impeller 1 of FIG. 1 and the compressor housing containing the symmetric compressor impeller 1. 6 is adopted, and the turbo side constituted by the symmetric turbine impeller 98 and the turbine housing 99 containing the symmetric turbine impeller 98 includes the symmetric turbine impeller 63 of FIG. Since the structure substantially the same as that of the turbine housing 69 containing the symmetrical turbine impeller 63 is employed, the description of each part relating to the compressor side and the turbo side is omitted. Furthermore, since the exhaust system employs the same configuration as that of the exhaust pipe in FIG. 6, description of each part is omitted.

Next, the operation will be described with reference to FIG.
In the turbocharger 100 configured as described above, when starting or rotating at a low speed, the first switching valve 104 blocks communication between the second exhaust pipe 105 and the other turbine housing 106, and the first series of through holes By continuing to stop at the position where 107 is kept open, the first exhaust pipe 108 and the second trachea 105 are kept in communication.
Further, the second switching valve 109 continues to stop at the position where the second communication hole 110 is opened, and the second exhaust pipe 105 and the third exhaust pipe 111 are communicated with each other. Block communication.

  Therefore, an exhaust path is constructed in which the exhaust gas guided by the second exhaust pipe 105 flows into the exhaust gas guided by the first exhaust pipe 108, and the exhaust gas discharged from one turbine housing 112 passes through the third exhaust pipe 111. An exhaust path that flows into the other turbine housing 106 is established.

  Then, all the exhaust gas discharged from the engine is supplied from the first exhaust pipe 108 side to one turbine impeller 113 included in one turbine housing 112, and the second exhaust pipe 105 and the third exhaust pipe 111. Since they are in communication with each other, the exhaust gas after rotating one turbine impeller 113 included in one turbine housing 112 is supplied to the other turbine impeller 114 included in the other turbine housing 106.

  By rotating one turbine impeller 113 and then flowing into the other turbine housing 106 and rotating the other turbine impeller 114, the symmetric turbine impeller 98 rotates vigorously, and further, one compressor impeller 115 and the other In the symmetric compressor impeller 96 constituted by the compressor impeller 116, one of the compressor impellers 115 accelerates the air sucked from the air suction port 117 and supercharges it to the engine side from the air discharge port 118, and the air suction port 119. The other compressor impeller 116 is accelerated by the other compressor impeller 116 and is supercharged from the air discharge port 118 to the engine side.

Further, when the engine speed increases and a preset switching time is reached, the first switching valve 104 continues to stop at a position where the first through hole 107 is kept closed, so that the first exhaust pipe 108 and the first switching valve 104 are stopped. Communication between the two exhaust pipes 105 is cut off, the first exhaust pipe 108 establishes an exhaust gas path communicating with one turbine housing 112, and the second exhaust pipe 105 communicates with the other turbine housing 106. A route is built.
Further, the second switching valve 109 continues to stop at a position where the second communication hole 110 is closed, and the communication between the second exhaust pipe 105 and the third exhaust pipe 111 is shut off. An exhaust gas path communicating with the atmosphere is constructed, and the second exhaust pipe 105 is constructed with an exhaust gas path communicating with the other turbine housing 106, and after rotating the other turbine impeller 114, the fourth exhaust Released from the tube 94 into the atmosphere.

  Therefore, the exhaust gas guided to the first exhaust pipe 108 continues to be supplied to one turbine impeller 113 included in one turbine housing 112, and the exhaust gas guided to the second exhaust pipe 105 Since the exhaust gas that is supplied to the other turbine impeller 114 included in the turbine housing 106 and passes through one turbine impeller 113 or the other turbine impeller 114 flows without clogging even in the high speed rotation region, the one turbine impeller 113 or the other The turbine impeller 114 and the symmetrical compressor impeller 96 disposed and fixed on the rotating shaft also rotate and increase vigorously, and the supercharging effect can be enhanced even in the high speed rotation range.

  Since the turbocharger 100 of FIG. 9 adopts the above-described configuration, the turbocharger main body can be made compact and lightweight, and the supercharging effect is enhanced by reducing the diameters of the symmetric compressor impeller 96 and the symmetric turbine impeller 98, Engine response, torque and output can be increased from low to medium speed to high speed.

  On the turbo side of each turbocharger described above, when the first series of holes and the first switching valve, the second communication hole and the second switching valve, etc. are provided, the first switching valve and the second switching valve are opened and closed. By doing so, the exhaust gas path was controlled and the supercharging effect in each rotation range was enhanced, but there was no special provision on the compressor side.

  However, the first exhaust pipe provided on the turbo side also on the compressor side, which is composed of a symmetric compressor impeller and a compressor housing containing the symmetric compressor impeller, in order to obtain even higher torque at the time of starting or at low speed rotation , The second exhaust pipe, the third exhaust pipe, and the first intake pipe, the second intake pipe, the third corresponding to the first series of holes and the first switching valve, the second communication hole and the second switching valve, etc. An intake pipe that is further provided with an intake pipe, a third communication hole and a third switching valve, a fourth communication hole and a fourth switching valve, etc., for supplying air pressurized by one compressor impeller to the other compressor impeller and further pressurizing it By constructing the turbocharger, a turbocharger 120 that can obtain a high supercharging pressure when starting or rotating at a low speed is also conceivable.

  FIG. 10 shows an embodiment thereof. On the compressor side, one compressor impeller 126 is disposed between both sides of a hub 124 supported by the rotary shaft 123 and a back plate portion 125 formed in a circular shape from the central portion of the hub. And the other compressor impeller 127 are arranged back to back with the back plate portion 125 in between, and the hub 124, the back plate portion 125, one compressor impeller 126, and the other compressor impeller 127 are integrated. A symmetric compressor impeller 121 and a compressor housing 122 containing the symmetric compressor impeller 121 are included.

  Further, the back plate portion 125 is arranged inside the compressor housing 122 enclosing the symmetric compressor impeller 121 into one compressor housing 128 containing one compressor impeller 126 and the other compressor housing 129 containing the other compressor impeller 127. In order to divide into two as much as possible, it is formed in a circular shape radially from the center of the hub, and on the side of the compressor housing 122 facing the outer periphery of the back plate 125, there is a slight gap with the outer periphery of the back plate 125. A partition plate 130 is provided.

Further, in the partition plate 130 provided on the compressor housing 122 side, the partition plate 130 is manufactured by integrally molding with the compressor housing 122 main body, or the partition plate 130 is manufactured in advance as a single unit, and the partition plate 130 is assembled when the compressor housing 122 is assembled. A method of sandwiching and integrating them by screws, fittings, or the like is conceivable. When the partition plate 130 is manufactured in advance as a single unit, the thickness of the partition plate 130 can be set thin.
As the manufacturing method of the partition plate 130, the same manufacturing method may be adopted in the compressor housing in FIGS. 3 to 5 including FIG. 1, the turbine housing in FIG. 6, and the compressor housing and the turbine housing in FIGS. .

  The one compressor housing 128 is formed with one air chamber 132 surrounding the air suction port 131 of one compressor impeller 126, and a first air introduction pipe 133 communicates with and is fixed to the one air chamber 132. In addition, the first intake pipe 135 is connected and fixed to the air discharge port 134 of the air pressurized by one compressor impeller 126.

  Further, the other compressor housing 129 is formed with the other air chamber 137 surrounding the air suction port 136 of the other compressor impeller 127, and a second air introduction pipe 138 communicates with and is fixed to the other air chamber 137. In addition, the second intake pipe 140 is connected and fixed to the air discharge port 139 of the air pressurized by the other compressor impeller 127, and the first intake pipe 135 and the second intake pipe 140 are joined together. A fourth intake pipe 141 is connected to the engine side.

A third intake pipe 142 communicating with the other air chamber 137 is connected to the first intake pipe 135, and a third communication hole 143 communicating with the first intake pipe 135 and the third intake pipe 142 is connected to the first intake pipe 135. A third switching valve 144 that opens and closes communication between the first intake pipe 135 and the third intake pipe 142 is provided, and the third intake pipe 142 communicates with the other air chamber 137 in the fourth communication hole 145. A fourth switching valve 146 that opens and closes communication between the one intake pipe 131 and the third intake pipe 137 is provided.
The third communication hole 143 and the third switching valve 144 are provided on the near side where the first intake pipe 135 and the second intake pipe 140 merge.

  The third switching valve 144 continues to stop at a position where the third communication hole 143 is opened when starting or rotating at a low speed, blocking communication between the first intake pipe 135 and the fourth intake pipe 141, When the fourth switching valve 146 continues to stop at the position where the fourth communication hole 145 is opened, the air pressurized by one compressor impeller 126 is supplied to the other compressor impeller 127 via the third intake pipe 142. An intake path is established.

  Therefore, on the turbo side at the time of start or low speed rotation, exhaust gas exhausted from all the cylinders is supplied to the first turbine impeller 147 in FIG. 10 as in the turbo side in the embodiment of FIGS. Since the exhaust passage is constructed, the first turbine impeller 147 having a reduced diameter and a reduced inertia force rotates and rises vigorously, the second switching valve 148 is also opened, and the second communication hole 149 is closed. As a result, an exhaust passage communicating between the third exhaust pipe 150 and the second turbine housing 151 is constructed, and after the first turbine impeller 147 is rotated, the exhaust gas still having energy is The turbine housing 151 is supplied to the second turbine impeller 152 contained therein, and has the first turbine impeller 147 and the second turbine impeller 152. Generic type turbine impeller 153 vigorously rotates increases.

On the compressor side, the air accelerated by one compressor impeller 126 is supplied to the other compressor impeller 127 from the air intake port 136 through the third intake pipe 142 and further accelerated, and the boost pressure is increased. Air is supplied from the second intake pipe 140 to the engine side via the fourth intake pipe 141.
Therefore, the supercharging effect can be further enhanced when starting or rotating at a low speed, and a high torque can be obtained.

Further, when the engine speed increases and the preset switching time is reached, the third switching valve 144 continues to stop at the position where the third communication hole 143 is closed, and the first intake pipe 135 and the fourth intake valve are stopped. An intake path is formed in which the pipe 141 is communicated and one compressor impeller 126 flows the accelerated air to the fourth intake pipe 141, and the accelerated air is supplied to the engine side via the fourth intake pipe 141. An intake path is constructed in which the fourth switching valve 146 continues to stop at a position where the fourth communication hole 145 is closed, and the air accelerated by the other compressor impeller 127 flows from the second intake pipe 140 to the fourth intake pipe 141. The accelerated air is supplied to the engine side through the fourth intake pipe 141.
Therefore, the supercharging effect can be enhanced over the entire rotation range, and the engine response, torque and output can be further increased from the low to medium speed rotation range to the high speed rotation range.

  In the symmetric compressor impeller 121, the dimensions, blade shapes, etc. of one compressor impeller 126 and the other compressor impeller 127 are unified with the specifications such as the dimensions, blade shapes, etc. with the back plate portion 125 as the center plane. In particular, in order to increase the supercharging pressure at the time of starting or at low speed rotation, the air pressure accelerated by one compressor impeller 126 is accelerated by the other compressor impeller 127, and the dimensions and blade shapes are used. It is recommended to set each compressor impeller to a specification adapted to the output characteristics required for the engine.

  For the turbo side in the turbocharger 120 described above, the same configuration as that of the turbo side of the turbocharger 100 shown in FIG. 9 was adopted. Therefore, description of the turbo side configuration and the like is omitted.

  The symmetric compressor impeller 121 is screwed to one end of the rotating shaft 123, and the symmetric turbine impeller 153 is joined to the other end of the rotating shaft 123. The rotating shaft 123 is a bearing / seal mechanism in the bearing housing 154. Thus, the bearing / seal mechanism is further lubricated and cooled by circulating oil from the outside.

  In the turbocharger 100 shown in FIG. 9 and the turbocharger 120 shown in FIG. 10 described above, a configuration in which a symmetric compressor impeller and a symmetric turbine impeller are respectively arranged and fixed at both ends of a rotating shaft supported by a bearing housing. As a result of the adoption, the above-described effects can be ensured, and the turbocharger body can be made compact, and the degree of freedom in design increases with respect to the arrangement position of the turbocharger body, the arrangement position of the engine body equipped with the turbocharger, and the like.

  Further, the above-described symmetric compressor impeller 121, the compressor housing 122 containing the symmetric compressor impeller 121, the first intake pipe 135, the second intake pipe 140, the third intake pipe 142, and the third communication hole 143 are also described. Further, a turbocharger in which the compressor side configured by providing the third switching valve 144, the fourth communication hole 145, the fourth switching valve 146, etc. is adopted and combined with the compressor side in each turbocharger described above is also conceivable.

  In addition to the twin turbine turbocharger 3 described above, in the symmetric turbine turbocharger 62, the turbocharger 100, the turbocharger 120, etc., the first exhaust pipe, the second exhaust pipe, the first switching valve, The object of the present application can be achieved by providing a series of through holes, a second switching valve, a second communication hole, a third exhaust pipe, and the like. For the second exhaust pipe, the first switching valve, the first series of holes, the second switching valve, the second communication hole, the third exhaust pipe, etc., specifications suitable for each engine are required. .

  Therefore, in the turbocharger main body, the first exhaust pipe and the second exhaust pipe, the first switching valve, the first series hole, the second switching valve, the second communication hole, the third exhaust pipe, etc. 1 and the compressor housing containing the symmetric compressor impeller and the rotating shaft at the boundary of CC ′, DD ′, GG ′, and HH ′ in FIG. The portion constituted by the bearing housing that performs the operation, the turbine housing that contains the turbine impeller, etc. is the turbocharger body, and the first exhaust pipe and the second exhaust pipe, the first switching valve, the first series of holes, A case where the two switching valve, the second communication hole, the third exhaust pipe, and the like are manufactured separately and mounted on the engine in combination with the turbocharger main body is conceivable.

Further, on the compressor side shown in FIG. 10 as well, the first intake pipe, the second intake pipe, the third intake pipe, the third communication hole, the third switching valve, and the fourth communication hole, similarly to the turbocharger main body described above. The first intake pipe, the second intake pipe, the third intake pipe, the third communication hole and the third switching valve, the fourth communication hole and the fourth switching When the valve is manufactured separately and mounted on the engine in combination with a turbocharger body that consists of a compressor housing that contains the compressor impeller, a bearing housing that supports the rotating shaft, and a turbine housing that contains the turbine impeller. Can be considered.
Therefore, the boundaries of the turbocharger main body, each exhaust pipe provided with each communication hole and each switching valve, and each intake pipe provided with each communication hole and each switching valve, etc. shall be set as appropriate, and each boundary is illustrated. Not.

  1 to 10 are schematic explanatory views, and therefore, including the shape of each part, the shape and handling of each exhaust pipe, the turbocharger main body, each exhaust pipe, each intake pipe, etc. Various modifications can be made to the borders, combinations, and the like without departing from the spirit of the present invention, and the present invention naturally extends to the modified ones.

Claims (5)

  A symmetrical compressor impeller in which one compressor impeller and the other compressor impeller are integrally configured back to back with the back plate interposed between both sides of a hub and a back plate formed radially from the hub central portion. And one air chamber that encloses the symmetric compressor impeller and surrounds the air intake port of the one compressor impeller is provided on the side surface of one compressor housing, and the other air chamber that surrounds the air intake port of the other compressor impeller An air chamber is provided on the side of the other compressor housing, and further, an air introduction port communicating with the one air chamber and the other air chamber, and an air discharge port for air pressurized by the symmetric compressor impeller are provided. The compressor side consisting of the compressor housing A first turbine housing containing a turbine impeller and provided with an exhaust gas introduction port and an exhaust gas discharge port, and a second turbine housing containing a second turbine impeller and provided with an exhaust gas introduction port and an exhaust gas discharge port, respectively. Arranged between the compressor housing and the first turbine housing, and between the compressor housing and the second turbine housing via a first bearing housing and a second bearing housing that support the rotating shaft. A twin turbine turbocharger characterized in that a symmetric compressor impeller is fixed at the center of the rotating shaft, and a first turbine impeller and a second turbine impeller are fixed at both ends of the rotating shaft.   A symmetrical compressor impeller in which one compressor impeller and the other compressor impeller are integrally configured back to back with the back plate interposed between both sides of a hub and a back plate formed radially from the hub central portion. And one air chamber that encloses the symmetric compressor impeller and surrounds the air intake port of the one compressor impeller is provided on the side surface of one compressor housing, and the other air chamber that surrounds the air intake port of the other compressor impeller An air chamber is provided on the side of the other compressor housing, and further, an air introduction port communicating with the one air chamber and the other air chamber, and an air discharge port for air pressurized by the symmetric compressor impeller are provided. Compressor side composed of the compressor housing A turbo side constituted by a turbine housing including a bin impeller and provided with an exhaust gas introduction port and an exhaust gas discharge port is integrally formed through a bearing housing that supports a rotation shaft, and a symmetric compressor is provided at both ends of the rotation shaft. A single turbine turbocharger characterized in that the impeller and the turbine impeller are fixed respectively.   Symmetrical configuration in which one turbine impeller and the other turbine impeller are integrated back-to-back with the back plate portion between both sides of a hub and a back plate portion formed radially and circularly from the hub central portion. Type turbine impeller and the symmetric turbine impeller so that the inside of the turbine housing is divided into one turbine housing and the other turbine housing as much as possible by the outer periphery of the back plate portion of the symmetric turbine impeller. The inner peripheral surface is shaped to maintain a slight gap from the outer periphery of the back plate portion, and the one turbine housing and the other turbine housing are provided with dedicated exhaust gas inlets, respectively, and the one turbine One exhaust gas chamber surrounding the impeller exhaust gas discharge port is located on the side of one turbine housing A turbine housing configured such that the other exhaust gas chamber surrounding the exhaust gas discharge port of the other turbine impeller is provided on a side surface of the other turbine housing, and the exhaust gas introduction port of the one turbine housing The first exhaust pipe is fixed, the second exhaust pipe is fixed to the exhaust gas inlet of the other turbine housing, and the exhaust gas flowing through each of the first exhaust pipe and the second exhaust pipe is in the same direction. In the flowing AA ′ portion, there is provided a first series of holes communicating the first exhaust pipe and the second exhaust pipe, and a first switching valve for switching the first series of holes to an open state or a closed state. The third exhaust pipe is fixed to one exhaust gas chamber surrounding the exhaust gas discharge port of one turbine impeller, and the exhaust gas flowing through each of the third exhaust pipe and the second exhaust pipe flows in the same direction. B 'part A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe, and a second switching valve that switches the second communication hole to an open state or a closed state. The turbo side, which is configured with a fixed exhaust pipe, includes a first compressor impeller, a first compressor housing having an air inlet and an air outlet, and a second compressor impeller, and an air inlet and an air outlet. A first bearing housing that is arranged in the center of the compressor side that is constituted by a second compressor housing provided with an outlet, and that supports a rotating shaft between the turbine housing and the first compressor housing and between the turbine housing and the second compressor housing. And the second bearing housing, and is symmetrical with respect to the center of the rotation axis. The turbine impeller is fixed, symmetric turbine turbocharger that the first compressor impeller and the second single compressor impeller, characterized in that fixed to the rotating shaft at both ends.   Symmetrical configuration in which one turbine impeller and the other turbine impeller are integrated back-to-back with the back plate portion between both sides of a hub and a back plate portion formed radially and circularly from the hub central portion. Type turbine impeller and the symmetric turbine impeller so that the inside of the turbine housing is divided into one turbine housing and the other turbine housing as much as possible by the outer periphery of the back plate portion of the symmetric turbine impeller. The inner peripheral surface is shaped to maintain a slight gap from the outer periphery of the back plate portion, and the one turbine housing and the other turbine housing are provided with dedicated exhaust gas inlets, respectively, and the one turbine One exhaust gas chamber surrounding the impeller exhaust gas discharge port is located on the side of one turbine housing A turbine housing configured such that the other exhaust gas chamber surrounding the exhaust gas discharge port of the other turbine impeller is provided on a side surface of the other turbine housing, and the exhaust gas introduction port of the one turbine housing The first exhaust pipe is fixed, the second exhaust pipe is fixed to the exhaust gas inlet of the other turbine housing, and the exhaust gas flowing through each of the first exhaust pipe and the second exhaust pipe is in the same direction. In the flowing AA ′ portion, there is provided a first series of holes communicating the first exhaust pipe and the second exhaust pipe, and a first switching valve for switching the first series of holes to an open state or a closed state. The third exhaust pipe is fixed to one exhaust gas chamber surrounding the exhaust gas discharge port of one turbine impeller, and the exhaust gas flowing through each of the third exhaust pipe and the second exhaust pipe flows in the same direction. B 'part A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe, and a second switching valve that switches the second communication hole to an open state or a closed state. One compressor impeller and the other compressor impeller sandwich the back plate portion between the turbo side formed by fixing the exhaust pipe, the hub, and both side surfaces of the back plate portion radially formed from the hub central portion. A symmetrical compressor impeller integrally configured back-to-back, and one air chamber that surrounds the air suction port of the one compressor impeller and is provided on one side of the compressor housing. The other air chamber surrounding the air inlet of the other compressor impeller is provided on the side of the other compressor housing; The compressor side, which is composed of a compressor housing provided with an air introduction port communicating with the other air chamber and the other air chamber, and an air discharge port for air pressurized by the symmetric compressor impeller, supports the rotating shaft. A turbocharger comprising a bearing housing and a symmetric compressor impeller and a symmetric turbine impeller fixed to both ends of the rotating shaft.   Symmetrical configuration in which one turbine impeller and the other turbine impeller are integrated back-to-back with the back plate portion between both sides of a hub and a back plate portion formed radially and circularly from the hub central portion. Type turbine impeller and the symmetric turbine impeller so that the inside of the turbine housing is divided into one turbine housing and the other turbine housing as much as possible by the outer periphery of the back plate portion of the symmetric turbine impeller. The inner peripheral surface is shaped to maintain a slight gap from the outer periphery of the back plate portion, and the one turbine housing and the other turbine housing are provided with dedicated exhaust gas inlets, respectively, and the one turbine One exhaust gas chamber surrounding the impeller exhaust gas discharge port is located on the side of one turbine housing A turbine housing configured such that the other exhaust gas chamber surrounding the exhaust gas discharge port of the other turbine impeller is provided on a side surface of the other turbine housing, and the exhaust gas introduction port of the one turbine housing The first exhaust pipe is fixed, the second exhaust pipe is fixed to the exhaust gas inlet of the other turbine housing, and the exhaust gas flowing through each of the first exhaust pipe and the second exhaust pipe is in the same direction. In the flowing AA ′ portion, there is provided a first series of holes communicating the first exhaust pipe and the second exhaust pipe, and a first switching valve for switching the first series of holes to an open state or a closed state. The third exhaust pipe is fixed to one exhaust gas chamber surrounding the exhaust gas discharge port of one turbine impeller, and the exhaust gas flowing through each of the third exhaust pipe and the second exhaust pipe flows in the same direction. B 'part A second communication hole that communicates between the second exhaust pipe and the third exhaust pipe, and a second switching valve that switches the second communication hole to an open state or a closed state. One compressor impeller and the other compressor impeller are connected to the back plate between the both sides of the turbo side formed by fixing the exhaust pipe, the hub, and a back plate formed radially and circularly from the center of the hub. A symmetrical compressor impeller integrally configured back-to-back with a portion interposed therebetween, and the symmetrical compressor impeller including the outer periphery of the back plate portion of the symmetrical compressor impeller, one compressor housing and the other compressor The inner surface of the compressor housing is shaped to maintain a slight gap from the outer periphery of the back plate so that it is divided into two as much as possible. One air chamber surrounding the air inlet of the one compressor impeller is provided on one side of the compressor housing, and the other air chamber surrounding the air inlet of the other compressor impeller is provided on the side of the other compressor housing. A compressor housing comprising a dedicated air discharge port for air pressurized by one compressor impeller and an air discharge port for air pressurized by the other compressor impeller, and The first air introduction pipe is fixed to the one air chamber side, the first intake pipe is fixed to the air discharge port side, and the second air introduction pipe is fixed to the other air chamber side. A second intake pipe is fixed to the air discharge port side, and the first intake pipe and the second air introduction pipe are connected to a third intake pipe. A third switching valve that opens and closes communication between the first intake pipe and the third intake pipe is provided in a third communication hole that communicates with the trachea and communicates with the first intake pipe and the third intake pipe. A fourth switching valve for switching communication between the third intake pipe and the other compressor impeller or between the second air introduction pipe and the other compressor impeller is provided at a communication portion between the three intake pipes and the second air introduction pipe. The turbocharger is characterized in that the compressor side configured as described above is integrally formed through a bearing housing that supports a rotating shaft, and a symmetric compressor impeller and a symmetric turbine impeller are fixed to both ends of the rotating shaft.

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