JPH07127474A - Supercharging device for engine - Google Patents

Abstract

PURPOSE:To reduce the number of bearings to support a turbo rotary shaft, to reduce the size of a device, and to reduce the generation of rotation resistance as supercharging efficiency and acceleration are improved through division of a turbo rotary shaft into a shaft on the compressor side and a shaft on the turbine side. CONSTITUTION:A turbo rotary shaft is divided into a shaft 36 on the compressor side to which a compressor 26 on the intake side is fixed and a shaft 38 on the turbine side to which a turbine 28 on the exhaust side is fixed. The two shafts are intercoupled through a hydraulic clutch and the shaft 36 on the compressor side is caused to perform auxiliary drive through injection of working oil to a hydraulic turbine 43. A coupling part bearing 39 is located between the two shafts 36 and 38, the vicinity of a coupling spot is supported by an intermediate bearing 421, the shaft 36 on the compressor side is supported by a bearing 42C on the compressor side, and the shaft 38 on the turbine side is supported by a bearing 42T on the turbine side.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a supercharger for an engine equipped with a turbocharger.

[0002]

2. Description of the Related Art Conventionally, as a supercharging device for an engine equipped with a turbocharger, for example, Japanese Patent Publication No. 59-51649.
The one shown in Japanese Patent Publication is known. With this device,
A compressor provided on the intake side and a turbine provided on the exhaust side are connected by a turbo rotary shaft, the turbo rotary shaft is rotatably supported by a slide bearing, and a fluid turbine is provided in the middle of the turbo rotary shaft. By injecting oil into this fluid turbine, driving of the turbo rotary shaft is assisted.

[0003]

Since the compressor wheel and the turbine wheel (particularly the turbine wheel) in the above turbocharger have a large moment of inertia, sufficient responsiveness can be obtained by externally applying an auxiliary driving force thereto. In order to obtain it, a very large auxiliary driving force is required, and the device becomes large accordingly.

On the other hand, regarding the bearing that rotatably supports the turbo rotary shaft, it is required to reduce the number of installed bearings as much as possible so as to make the device compact and reduce the rotational resistance of the bearing.

In view of the above circumstances, the present invention divides the turbo rotary shaft into a compressor side shaft and a turbine side shaft to improve supercharging efficiency and acceleration, and to increase the number of bearings that support the turbo rotary shaft. An object of the present invention is to provide an engine supercharging device that can be reduced in size and the rotation resistance can be reduced.

[0006]

As a means for solving the above problems, the present invention provides a turbocharger equipped with a turbo rotary shaft for connecting a compressor and a turbine,
In a turbocharger for an engine, which is provided in this turbocharger and has an auxiliary drive means for assisting the drive of the turbo rotating shaft, the turbo rotating shaft is divided into a compressor side shaft and a turbine side shaft, and both shafts are A clutch means for switching between a state in which both shafts are connected so as to rotate integrally and a state in which both shafts are disengaged so that both shafts can rotate relative to each other is provided, and either one of the compressor side shaft and the turbine side shaft is provided. A recess is formed at the end on the connecting side, and an insertion portion to be inserted into the recess is formed at the other end on the connecting side, and a connecting portion bearing is provided between the insertion portion and the recess, and the recess and the insertion are formed. An intermediate bearing that supports either the compressor side shaft or the turbine side shaft is arranged near the section, and a compressor that supports the compressor side shaft between the intermediate bearing and the compressor. A bearing provided, is provided with a turbine side bearing which supports the turbine side shaft between the intermediate bearing and the turbine (claim 1).

Here, it is more preferable that the connecting portion bearing is a sliding bearing (claim 2), and the intermediate bearing, the compressor side bearing and the turbine side bearing are rolling bearings (claim 3). It is more preferable that the is composed of an angular ball bearing (claim 4).

Further, in the above apparatus, the auxiliary drive means is provided between the intermediate bearing and the compressor side bearing, and the clutch means is provided between the intermediate bearing and the turbine side bearing. (Claim 5)

[0009]

According to the apparatus of the present invention, when the turbine rotation speed is low, the compressor side shaft and the turbine side shaft are separated from each other, and only the compressor side shaft and the compressor having a small moment of inertia are auxiliary driven, and the turbine rotation speed is reduced. When the turbo rotation shaft is connected to the compressor side shaft and the turbine side shaft to start driving the turbo rotary shaft using exhaust gas energy, the turbo rotary shaft can be efficiently rotationally driven with a small auxiliary driving force. it can.

Here, the compressor side shaft is supported by the compressor side bearing and one of the intermediate bearing and the connecting portion bearing, and the turbine side shaft is the other of the turbine side bearing, the intermediate bearing and the connecting portion bearing. The turbo rotary shaft is supported from the outside by three of the compressor side bearing, the intermediate bearing, and the turbine side bearing.
Since there are only one bearing, the space for installation is reduced by the number of bearings thus reduced, the device is downsized, and the bearings that operate when both shafts are integrally connected (the above intermediate bearing, compressor The total sum of the rotational resistances of the side bearings and the turbine side bearings) is also reduced, and the required drive torque of the turbo rotating shaft is reduced.

Here, in the state where the compressor side shaft and the turbine side shaft are connected, the relative rotational speed of both is 0.
Therefore, if a rolling bearing is used as the above-mentioned connecting portion bearing arranged between both shafts, the stationary period of the rolling element in this rolling bearing becomes long, and the bearing performance may be deteriorated due to sticking of the rolling element or the like. However, in the device according to the second aspect, since the sliding bearing is used as the connecting portion bearing, there is no fear of that. Further, since the sliding bearing can have a smaller diameter than the rolling bearing, the connecting portion of both shafts can be downsized accordingly.

On the other hand, in the device according to the third aspect, since the intermediate bearing, the compressor side bearing and the turbine side bearing are constituted by rolling bearings, the rotation resistance is further increased as compared with the case where sliding bearings are used for these bearings. Be reduced. Particularly, when the angular ball bearing is used as described in claim 4, the rotation resistance can be further reduced and the thrust force acting on the turbo rotating shaft can be sufficiently supported.

Further, in the apparatus of the fifth aspect, the auxiliary driving means is provided between the intermediate bearing and the compressor side bearing, and the clutch means is provided between the intermediate bearing and the turbine side bearing. Therefore, these three bearings, auxiliary drive means, and clutch means are arranged with a minimum space.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to the drawings.

A common intake pipe 14 is connected to each cylinder of the engine 10 shown in FIG. 6 through an intake manifold 12, and a throttle valve 15, an intercooler 16, a turbocharger (actually described later A turbocharger 24, which also has a function as a supercharger that is auxiliary driven, an air cleaner 18, and the like are provided. Exhaust manifold 1 for each cylinder
A common exhaust pipe 20 is connected to the turbocharger 24 and the exhaust gas purifying catalyst 22 in the middle thereof.
Etc. are provided.

The internal structure of the turbocharger 24 is shown in FIGS. The turbocharger 24 includes a compressor 26 and a turbine 28, similar to a normal turbocharger. The compressor 26 is housed in a compressor housing 30, and the turbine 28 is housed in a turbine housing 32. The compressor housing 30 is incorporated in the middle of the common intake pipe 14,
The turbine housing 32 is incorporated in the middle of the common exhaust pipe 20, and the housings 30 and 32 are connected to each other via a substantially cylindrical main body housing 34.

Here, while the compressor 26 is configured to suck in fresh air in the axial direction and discharge it to the outside in the radial direction by the rotation thereof, the turbine 28 causes the exhaust gas to be discharged in the radial direction by the rotation thereof. It is configured to be sucked from the outside and discharged in the axial direction.

A compressor side shaft 36 and a turbine side shaft 38 are housed in the center of the main body housing 34 coaxially therewith. And the compressor side shaft 36
The outer end (the right end in FIG. 1) of the compressor 2 is
The outer end of the turbine-side shaft 38 (the left end in FIG. 1) is fixed to the center of the turbine 28.

An inner end portion (left end portion in FIG. 1) of the compressor side shaft 36 is a cylindrical portion (recess) 37 that opens toward the tip, and an inner end portion of the turbine side shaft 38 (right side in FIG. 1). An end portion) is formed with a small-diameter insertion portion 35 that is inserted into the cylindrical portion 37 so as to be relatively rotatable. A connecting portion bearing 39, which is a slide bearing, is interposed between the inserting portion 35 and the cylindrical portion 37. The connecting portion bearing 39
Is fixed to the insertion portion 35 side in this embodiment.

An outer cylinder 41 is fitted on the outer side in the radial direction of the compressor side shaft 36 so as to rotate integrally therewith,
A hydraulic turbine (fluid turbine) 43 is integrally formed at an appropriate position on the outer peripheral surface of the outer cylinder 41. The hydraulic turbine 43 has blades having a shape that converts this energy into rotational energy of the compressor-side shaft 36 by blowing a working oil flow having a circumferential component from the turbine side (left side in FIG. 1).

Inside the main body housing 34, a cylindrical bearing housing 40 is inserted which extends over substantially the entire axial direction thereof. As shown in FIG. 2, on the outer peripheral surface of the bearing housing 40, a large number of ribs 40a are arranged side by side in the axial direction along the entire circumference, and between the outer peripheral surface of these ribs 40a and the inner peripheral surface of the main body housing 34. A small gap is secured in.

Inside the bearing housing 40, the outer cylinder 41 outside the compressor side shaft 36 and the turbine side shaft 3 are provided.
Three bearings (angular ball bearings in this embodiment) 42I, 42C, 42T that rotatably support 8 and 8 are held. More specifically, an intermediate bearing 42I is provided at a position of the compressor-side shaft 36 that supports a portion near the cylindrical portion 37, and the compressor-side bearing 42 is provided inside the compressor-side end (the right end in FIG. 1) of the bearing housing 40.
C is provided, a turbine side bearing 42T is provided inside the turbine housing side end portion (left side end portion in FIG. 1) of the bearing housing 40, and the hydraulic turbine 43 is provided between the bearings 42I and 42C. .

The turbine side bearing 42T and the intermediate bearing 42
Between the compressor side 36 and the turbine side shaft 38
A hydraulic clutch (clutch means) 44 is provided for connecting / disconnecting to / from. This hydraulic clutch 44
Is composed of turbine side members 46 and 48, a compressor side member 50, a spacer ring 52, a positioning ring 53, a sleeve 54, etc. as shown in FIG.

The turbine-side members 46 and 48 are fitted onto the turbine-side shaft 38 and fixed with nuts 58.
The turbine side member 46 has a flange portion 46a at a substantially central portion in the axial direction. The turbine-side member 48 has a tapered surface 48a in the direction of decreasing the diameter from the turbine side to the compressor side on the side closer to the turbine 28, and a tapered surface 48b in the direction of decreasing the diameter from the compressor side to the turbine side. It has on the side close to 26. The compressor-side member 50 is mounted on the outer peripheral surface of the cylinder portion 37 of the compressor-side shaft 36 so as to be relatively movable only in the axial direction via a spline 59.
The tapered surface 48b of the turbine side member 48 is a tapered surface 50a having a shape capable of being brought into surface pressure contact with each other.

The sleeve 54 is the member 4 on the turbine side.
6, 48 and the outer peripheral surface of the compressor side member 50 are slidably fitted in the axial direction. An annular protrusion 54b is formed on the inner peripheral surface of the sleeve 54, and a hydraulic chamber 47 is formed between the annular protrusion 54b and the collar 46a of the turbine side member 46. The surface of the annular protruding portion 54b that faces the tapered surface 48a of the turbine-side member 48 is a tapered surface 54a that expands in diameter from the turbine side toward the compressor side, and between the tapered surfaces 48a and 54a. A plurality of balls 56 are sandwiched. A positioning ring 53 is fixed to the inside of the end of the sleeve 54 near the compressor 26, and the spacer ring 52 is sandwiched between the positioning ring 53 and the compressor-side member 50. The inner peripheral edge of the spacer ring 52 is in a state of directly contacting the compressor side end surface (the right end surface in FIG. 2) of the cylindrical portion 37.

When the ball 56 bites between the tapered surfaces 48a and 54a by centrifugal force, the sleeve 54 and the positioning ring 53 move toward the turbine 28 (leftward in FIG. 2) due to the biting. Then, the compressor-side member 50 is pulled toward the turbine side via the spacer ring 52, whereby the compressor-side member 50
The tapered surface 50a of the turbine-side member 48 and the tapered surface 48b of the turbine-side member 48 are pressed against each other so as to rotate together, while hydraulic pressure is supplied to the hydraulic chamber 47, and centrifugal force and bite of the ball 56 are generated. In a weak state, the sleeve 54 is forcibly pushed back to the compressor side, the tapered surfaces 50a and 48b are separated from each other in the axial direction, and the pressure contact and the axial connection are released.

Next, the oil passage of the working oil formed in the turbocharger 24 will be described. In this embodiment, the working oil is also used as the lubricating oil and damping oil for each bearing.

In the bearing housing 40, a hydraulic oil injection block 60 as shown in FIGS. 3 to 5 is provided at a position adjacent to the hydraulic turbine 43. On the outer peripheral surface of the hydraulic oil injection block 60, the groove 6 extending over the entire circumference
2 are formed, and a plurality of (four in the illustrated example) injection holes 66 are formed from the groove 62 in a direction including a circumferential component and an axial component. It opens toward the hydraulic turbine 43.
Further, a nozzle insertion recess 64 as shown in FIGS. 2 and 3 is formed at an appropriate position on the peripheral portion of the groove 62.

On the other hand, a hydraulic oil supply nozzle 70 that penetrates the main body housing 34 in the radial direction is fixed, and the hydraulic oil supply nozzle 70 and the hydraulic oil injection block 60 constitute a fluid injection member. Has been done. The hydraulic oil supply nozzle 70 has a small-diameter tip portion 72. The small-diameter tip portion 72 penetrates a side wall of the bearing housing 40 closer to the compressor 26 than the hydraulic clutch 44, and the nozzle of the hydraulic oil injection block 60. Insertion recess 64
It is fitted inside, and the relative position of the bearing housing 40 in the axial direction with respect to the main body housing 34 is regulated by the penetration of the nozzle insertion recess 64.

A through hole 73 is formed in the side wall of the hydraulic oil supply nozzle 70. The through hole 73, the oil passage 74 formed in the main body housing 34, the oil passage 76 formed in the bearing housing 40, and the turbine. It communicates with the hydraulic chamber 47 through an oil passage 77 formed in the side member 46, an oil passage 78 formed in the turbine side shaft 38, and an oil passage 79 formed in the turbine side member 46.

A through hole 54c is provided in the side wall of the sleeve 54, a radial groove 52a is formed in the spacer ring 52, and the outer peripheral surface of the compressor side shaft 36 communicates with the inside of the cylindrical portion 37. Communicating passage 36a is formed, and these through holes 54c, groove 52a, and communicating passage 36 are formed.
The hydraulic oil outside the hydraulic clutch 44 is supplied to the coupling portion bearing 39 as lubricating oil through a.

In FIGS. 1 and 2, 80 and 82 are oil discharge ports for appropriately discharging the oil in the bearing housing 40 and the main body housing 34 to the outside of the main body housing 34.

Returning to FIG. 6, a hydraulic pump 108 is connected to the crankshaft 102 of the engine 10 via a drive transmission mechanism 104 and a pump clutch 106, and the hydraulic pump 108 is operated by the hydraulic valve 108 via a pressure regulating valve 110. It is connected to the supply nozzle 70. The hydraulic pump 108 operates by receiving the driving force of the crankshaft 102,
The lubricating oil in 0 is hydraulically sent to the hydraulic oil supply nozzle 70 via the pressure regulating valve 110.

This engine includes the compressor 26
Compressor rotation speed sensor 112 for detecting the rotation speed Nc per unit time, turbine rotation speed sensor 114 for detecting the rotation speed Nt of the turbine 28 per unit time, and a throttle sensor for detecting the throttle opening θ of the throttle valve 15. 116, an engine speed sensor 117 that detects the engine speed Ne, an engine intake pipe boost sensor 118 that detects the intake pipe internal pressure, and the like, and these sensors are connected to an ECU (control unit) 120. The ECU 120 controls the pump clutch 106 according to the engine speed Ne and the acceleration state of the engine.
Is configured to perform on / off control.

Next, the operation of this device will be described.

First, the control signal is output from the ECU 120 during low-speed acceleration and the pump clutch 106 is switched on, whereby the hydraulic pump 108 operates and the lubricating oil in the engine 10 is adjusted to a constant pressure by the pressure regulating valve 110. After being pressurized, the hydraulic oil supply nozzle 7 of the turbocharger 24
Supplied to zero. This hydraulic oil is the hydraulic oil injection block 6
It is injected in the circumferential direction from the injection port 68 toward the hydraulic turbine 43 through the groove 62 of 0 and each injection hole 66, and thereby the compressor side shaft 36 and the compressor 26 are driven to rotate integrally with the outer cylinder 41.

On the other hand, the working oil introduced from the working oil supply nozzle 70 is passed through the through hole 73, the oil passages 74, 76, 77,
It is introduced into the hydraulic chamber 47 through 78 and 79 in order. Here, when the turbine speed Nt is low, the balls 56
Since the centrifugal force that acts on the ball 56 is weak, the sleeve 48 and the positioning ring 53, which receive the hydraulic pressure of the hydraulic chamber 47, move to the compressor side (the right side in FIG. 2) while pushing out the ball 56 with the tapered surfaces 48a and 54a. Therefore, the tapered surface 50a of the compressor-side member 50 and the tapered surface 48b of the turbine-side member 48 are axially separated from each other and the pressure contact between them is released, and the compressor-side shaft 36 and the turbine-side shaft 38 are separated from each other. Separated so that they can rotate relative to each other.

That is, the supply of the hydraulic oil causes the compressor-side shaft 36 and the turbine-side shaft 38 to be separated from each other almost simultaneously with the rotational driving of the hydraulic turbine 43. As a result, only the compressor-side shaft 36 and the compressor 26 are driven to perform auxiliary rotation, and this rotation causes supercharging of the engine 10.

When the turbine speed Nt rises above a certain level while the acceleration proceeds in this manner, the centrifugal force acting on the ball 56 also increases, so that the ball 56 resists the pressure in the hydraulic chamber 47 and is tapered. Biting between the surfaces 48a and 54a, the sleeve 54 and the positioning ring 53 are moved toward the compressor 26 (to the left in FIG. 2), and the compressor side member 5 is moved through the spacer ring 52.
0 is drawn to the turbine side. As a result, the tapered surface 50a of the compressor-side member 50 and the turbine-side member 48
The tapered surface 48b of the compressor is in pressure contact, and the frictional force due to this pressure causes the compressor-side shaft 36 and the turbine-side shaft 38 to be coaxially connected to each other in a non-rotatable manner.

Therefore, in this state, as in the conventional turbocharger, the turbine 28 by the energy of the exhaust gas is used.
Is transmitted to the intake-side compressor 26 via both shafts 38 and 36 which are connecting shafts, and the rotation of the compressor 26 causes supercharging of each cylinder of the engine.

As described above, in this device, the turbo rotating shaft is divided into the compressor side shaft 36 and the turbine side shaft 38, and both are connected and disconnected by the hydraulic clutch 44. Therefore, the turbine speed Nt Is low, the compressor-side shaft 36 and the turbine-side shaft 38 are separated, and only the compressor 26 and the compressor-side shaft 36 having a small moment of inertia are auxiliary driven, and when the turbine speed Nt increases, the compressor-side shaft 36 and the turbine By connecting the side shaft 38 and starting driving of the turbo rotary shaft using the exhaust gas energy, the turbo rotary shaft can be efficiently rotationally driven with a small auxiliary driving force, and supercharging efficiency and acceleration performance can be improved. Significant improvement can be achieved.

Moreover, the compressor side shaft 36 is supported by two bearings of the compressor side bearing 42C and the intermediate bearing 42I, and the turbine side shaft 38 is supported by the two bearings of the turbine side bearing 42T and the coupling portion bearing 39. However, only three of the compressor-side bearing 42C, the intermediate bearing 42I, and the turbine-side bearing 42T support the entire turbo rotary shaft from the outside. Therefore, when the turbo rotary shaft is supported by four bearings. Compared with, the space required for installing the bearing can be reduced, and the device can be downsized. Particularly, in this embodiment, the compressor side bearing 4
The fluid turbine 43, the hydraulic oil injection block 60, and the hydraulic oil supply nozzle 70 are provided between the 2C and the intermediate bearing 42I, and the hydraulic clutch 44 is provided between the turbine side bearing 42T and the intermediate bearing 42I. , These components are reasonably arranged with minimal space.

Further, by reducing the number of bearings (bearings 42C, 42I, 42T) that operate in a state where both shafts 36, 38 are connected, the total sum of the rotational resistances of these bearings also becomes small, and the turbo resistance is reduced accordingly. The drive torque required for the rotating shaft is also reduced. Moreover, in this embodiment, the bearing 4
Since the angular ball bearings are used for the 2C, 42I, and 42T, the rotation resistance can be further reduced and the thrust force acting on the turbo rotating shaft can be supported with sufficient strength.

On the other hand, since a plain bearing having a relatively small radial dimension is used for the connecting portion bearing 39, the two shafts 3
It is possible to reduce the size of the connecting portions of 6, 38. Further, since the relative rotation speed of the two shafts 36, 38 is 0 when they are connected, when a rolling bearing is used as the connecting portion bearing 39, the rolling elements in the rolling bearing are rotated when the shafts 36, 38 rotate. Remains stationary, and the inconvenience of sticking of the rolling elements is likely to occur due to the longer rest time of the rolling elements, and there is a risk that good bearing performance may not be obtained when the shafts 36, 38 are separated. However, in this embodiment, since a slide bearing is used as the coupling portion bearing 39, even if the relative speed of the shafts 36 and 38 remains zero for a long period of time, the bearing performance thereafter is not impaired.

The present invention is not limited to the above embodiments, but the following modes can be adopted as examples.

(1) For the bearings 42C, 42I, 42T, the rolling resistance can be reduced by using other rolling bearings in addition to the angular ball bearings. However, among these, the use of the ball bearing has an advantage that the rotational resistance can be further reduced. Further, for the coupling portion bearing 39, a needle bearing or the like can be applied in addition to the above sliding bearing.

(2) In the above embodiment, the compressor side shaft 3
Although the cylindrical portion 37, which is a concave portion, is provided at 6 and the insertion portion 35 is provided at the turbine side shaft 38, conversely, the insertion portion may be provided at the compressor side shaft 36 and the concave portion may be provided at the turbine side shaft 38. .

(3) In the above embodiment, the compressor side shaft 3
Although 6 is supported by the intermediate bearing 42I, the turbine side shaft 38 may be supported by the intermediate bearing 42I.

(4) The clutch means for connecting / disconnecting the two shafts 36, 38 is not limited to the hydraulic clutch 44 as described above.
It is possible to use various customary clutches that can be engaged and disengaged.

[0050]

As described above, according to the present invention, the turbo rotating shaft is divided into the compressor side shaft and the turbine side shaft, and the clutch means for switching the two to the connected state and the disconnected state is provided. When the speed is low, the compressor-side shaft and the turbine-side shaft are separated, and only the compressor-side shaft and compressor with a small moment of inertia are auxiliary driven, and the compressor-side shaft and turbine-side shaft are connected when the turbine rotation speed increases. Then, by starting the drive of the turbo rotary shaft using the exhaust gas energy,
The turbo rotating shaft can be efficiently rotationally driven with a small auxiliary driving force.

In addition, by providing a connecting portion bearing between the compressor side shaft and the turbine side shaft and providing an intermediate bearing in the vicinity of the connecting portion, the entire turbo rotary shaft composed of both shafts is provided with the intermediate bearing and the compressor side bearing. , And the turbine side bearing are only supported from the outside, so that the number of bearings is small, the installation space is reduced and the device is downsized.
It is possible to reduce the total rotation resistance of each bearing and reduce the required drive torque of the turbo rotary shaft.

Here, since the relative rotational speed is 0 when both shafts are connected, when a rolling bearing is used for the connecting portion bearing, the rolling element in the rolling bearing is stationary when both shafts rotate. However, there is a possibility that inconvenience such as sticking of the rolling elements may occur, and good bearing performance may not be obtained when the two shafts are separated. However, in the device according to claim 2, a sliding bearing is provided for the coupling portion bearing. I am using
Even if the relative speed of both shafts remains zero for a long time, the bearing performance thereafter is not impaired. Further, since the sliding bearing can have a smaller diameter than the rolling bearing, the connecting portion of both shafts can be downsized accordingly.

On the other hand, in the device according to the third aspect, since the intermediate bearing, the compressor-side bearing, and the turbine-side bearing are constituted by rolling bearings, the rotation resistance is further increased as compared with the case where sliding bearings are used for these bearings. Can be reduced. In particular,
When the angular ball bearing is used as described in the fourth aspect, it is possible to further reduce the rotational resistance and to sufficiently support the thrust force acting on the turbo rotary shaft.

Further, in the apparatus according to claim 5, the auxiliary drive means is provided between the intermediate bearing and the compressor side bearing, and the clutch means is provided between the intermediate bearing and the turbine side bearing, respectively. There is an effect that these three bearings, auxiliary drive means, and clutch means can be arranged in a minimum space.

[Brief description of drawings]

FIG. 1 is an overall sectional view of a turbocharger according to an embodiment of the present invention.

FIG. 2 is a partially enlarged view of FIG.

FIG. 3 is a cross-sectional side view of a hydraulic oil injection block provided in the turbocharger.

FIG. 4 is a view on arrow A in FIG.

5 is a sectional view taken along line BB of FIG.

FIG. 6 is an overall configuration diagram of an engine including the turbocharger.

[Explanation of Codes] 10 Engine 24 Turbocharger 26 Compressor 28 Turbine 35 Insertion part 36 Compressor side shaft 37 Cylindrical part (recess) 38 Turbine side shaft 39 Coupling part bearing 42C Compressor side bearing 42I Intermediate bearing 42T Turbine side bearing 43 Hydraulic turbine ( Fluid turbine) 44 Hydraulic clutch (clutch means) 60 Hydraulic oil injection block (fluid injection means) 70 Hydraulic oil supply nozzle (fluid injection means)

Claims (5)

[Claims] 1. A turbocharger for an engine, comprising: a turbocharger having a turbo rotary shaft connecting a compressor and a turbine; and an auxiliary drive means provided on the turbocharger for assisting the drive of the turbo rotary shaft. In the above, the turbo rotary shaft is divided into a compressor side shaft and a turbine side shaft, and a state in which both shafts are connected so that both shafts rotate integrally and a state in which both shafts are separated so that both shafts can rotate relative to each other. And a clutch means for switching between the compressor side shaft and the turbine side shaft, and a recess is formed at an end of the connecting side of one of the compressor side shaft and the turbine side shaft, and an inserting portion is formed at the other side of the connecting side. , An intermediate shaft that provides a coupling bearing between the insertion part and the recess and supports either the compressor side shaft or the turbine side shaft in the vicinity of the recess and the insertion part. And a compressor-side bearing that supports the compressor-side shaft between the intermediate bearing and the compressor, and a turbine-side bearing that supports the turbine-side shaft between the intermediate bearing and the turbine. Characteristic engine supercharger. 2. The supercharging device for an engine according to claim 1, wherein the connecting portion bearing is a slide bearing. 3. The supercharging device for an engine according to claim 1, wherein the intermediate bearing, the compressor-side bearing, and the turbine-side bearing are rolling bearings. 4. The supercharging device for an engine according to claim 3, wherein the rolling bearing comprises an angular ball bearing. 5. The engine supercharger according to any one of claims 1 to 4, wherein the auxiliary drive means is provided between the intermediate bearing and the compressor-side bearing, and the intermediate bearing and the turbine-side bearing are provided. An engine supercharging device, characterized in that the clutch means is provided between them.