JP2003083245A - Combined driving type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a combined driving type compressor to a small size-in an axial direction and a radial direction. SOLUTION: A driving shaft 2 of the compressor 1 is driven not only by a main motive power source such as an engine loaded on a vehicle through a pulley 6 or the like but also by an electric motor 16 integrated with the compressor 1. Since the electric motor 16 is constituted utilizing a dead space formed on an outer periphery part of a main bearing 26 pivotally supporting the driving shaft 2, the compressor 1 is not made large by providing the electric motor 16. Since the pulley 6 is made to the one having a small diameter as compared with the case where the electric motor is provided at an end of the driving shaft 2 and the pulley 6 is provided on the outer periphery as conventional, it becomes easy that the compressor 1 is made small and is driven by a speed increase.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a plurality of power sources,
For example, a combined drive type compressor that can be rotationally driven alternatively or simultaneously by a main prime mover such as an internal combustion engine mounted on a vehicle and a subordinate prime mover such as an electric motor that is rotated by battery power. Staff, especially,
The present invention relates to a composite drive type compressor that can be downsized without reducing the discharge capacity.

[0002]

2. Description of the Related Art In recent years, an idle stop for stopping an internal combustion engine when a vehicle such as an automobile equipped with the internal combustion engine is stopped in order to cope with environmental problems or to reduce fuel consumption of the internal combustion engine. (Or eco-run) system is being put to practical use. If this system is used, the compressor of the vehicle air conditioner driven by the internal combustion engine will stop operating while the compressor is stopped, and as a result the air conditioner will stop operating. Therefore, an electric motor that is rotationally driven by the electric power stored in the battery is used, and while the vehicle is stopped, the power source is switched from the internal combustion engine to the electric motor to drive the compressor. A "hybrid compressor" has been proposed (Japanese Unexamined Patent Publication No. 20-29200).
No. 00-229516).

However, in such a hybrid compressor, the compressor and the electric motor are usually arranged in series in the axial direction, so that the axial lengths of the compressor and the electric motor are simply added, resulting in the hybrid. There is a problem in that the axial length of the compressor becomes extremely long, and the size of the compressor as a whole becomes large.

As a measure against this problem, an electric motor is housed in the internal space of a pulley attached to the drive shaft of the compressor to receive the power of the internal combustion engine into the compressor, thereby shortening the axial length of the hybrid compressor. A countermeasure has been proposed (see Japanese Patent Laid-Open No. 2001-140757), but in this case, since the pulley is provided on the outer periphery of the electric motor, the diameter of the pulley becomes very large.
In order to obtain a large discharge amount by operating a small-sized, small-capacity compressor at high speed, it is necessary to further increase the diameter of the drive pulley on the internal combustion engine side in order to increase the speed. Further, the pulleys of other auxiliary machines driven by the same internal combustion engine also need to have a large diameter, which is a great design constraint. Therefore, in a small-sized vehicle having no space, it is difficult to drive the small-sized compressor at an increased speed, and there is no choice but to mount a large-sized, large-capacity compressor.

[0005]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems in the prior art, and an object thereof is to solve these problems by a novel means.

[0006]

As a means for solving this problem, the present invention provides a compound drive type compressor described in claim 1 of the appended claims.

In the composite drive type compressor of the present invention, the dead space formed in the outer peripheral portion of the bearing of the compressor that supports the common drive shaft for a plurality of power sources is utilized, Since the electric motor is formed as a subordinate power source, the size of the entire compressor does not increase in both the radial direction and the axial direction even if the electric motor is attached to the compressor. Moreover, the diameter of the input means such as the pulley attached to the end of the drive shaft for the main power source such as the internal combustion engine mounted on the vehicle can be set small regardless of the outer diameter of the electric motor. As a result, it is possible to drive the compressor at an increased speed, and even with a compact, small-capacity compressor, a large discharge amount per unit time can be obtained. It becomes possible to mount it on.

In this case, the main body of the compressor, the electric motor formed on the outer peripheral portion of the bearing that axially supports the drive shaft, and the input means such as the pulley are sequentially arranged in the axial direction of the drive shaft. Is desirable. Also, input means such as pulleys,
An electromagnetic clutch can be provided inside.

The compound drive compressor of the present invention can be configured as a variable displacement compressor, which provides many advantages. In particular, when the variable capacity compressor is capable of operating at 0% capacity, if a one-way clutch is provided on the input means such as a pulley, it is not necessary to provide an electromagnetic clutch or the like on the drive shaft. The most preferable compound drive type compressor of the present invention is a scroll type compressor having a variable capacity function.

[0010]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment of Combined Drive Type Compressor of the Present Invention
As an example, FIG. 1 shows a combined drive type scroll compressor 1
The cross-sectional structure of is shown. In the flange portion 2a attached to the left end of the drive shaft 2 of the scroll compressor 1 in the drawing,
An annular hub 4 that is a driven-side rotating portion of the electromagnetic clutch 3 is connected via a disc-shaped or radial leaf spring 5.
Moreover, it is elastically supported so as to be slightly movable in the axial direction. The rotary portion 6 on the drive side of the electromagnetic clutch 3 also serves as a pulley for the belt by the annular groove formed in the outer peripheral portion. The support structure of the pulley 6 and the internal structure of the electromagnetic clutch 3 will be described later. The pulley 6 also serves as the outer shell of the electromagnetic clutch 3, and is also mounted on the crankshaft of an internal combustion engine (running engine mounted on the vehicle) (not shown), which is the main power source, via a belt (not shown). Driven to rotate.

The outer shell of the main body portion of the compound drive type scroll compressor 1 of the first embodiment comprises a front housing 7, a fixed scroll 8 connected to the rear portion, and a rear housing 9 connected to the rear portion. Has become. These members are integrated by means such as a through bolt 10. A second housing 11 is further mounted in front of the front housing 7 in order to support a driving portion of the scroll compressor 1. The pulley 6 is rotatably supported by a bearing 12 attached to the front end of the second housing 11. An iron core 15 including the coil 14 of the electromagnetic clutch 3 is attached to the front end surface of the second housing 11 so as to be located in the annular groove 13 of the pulley 6. When the coil 14 is electrically biased, the hub 4 described above is magnetically attracted and moves in the axial direction, so that the friction surface 6a at the front end of the pulley 6 can be slidably contacted and engaged. Therefore, the surface 4a of the hub 4 that contacts the friction surface 6a of the pulley 6 is also a friction surface.

Inside the second housing 11, an electric motor 16 is constructed as a secondary power source. In the first embodiment, a field iron core 17 as a stator is attached to the inner surface of the second housing 11, and a plurality of coils 18 are wound around it. The end of the coil 18 is connected to the connector 19. A cup-shaped rotor 20 is fixed to the drive shaft 2, and a plurality of permanent magnets 21 are attached to the outer periphery of the cup-shaped rotor 20 so as to face the field iron core 17. In the electric motor 16 configured in this way, three-phase AC power from the battery and the inverter is passed through the connector 18 to the coil 18 according to a command from an electronic control unit (not shown).
When it is supplied to the field iron core 17, a rotating magnetic field is generated in the field iron core 17. Therefore, the permanent magnet 21 follows the rotating magnetic field, so that the rotor 20 rotates and the drive shaft 2 of the scroll compressor 1 can be rotationally driven. .

In the main body of the scroll compressor 1, the fixed scroll 8 which constitutes a part of the housing as described above has a generally disk-shaped end plate portion 8a and a spiral which projects axially therefrom. The blade 8b is shaped like a blade. An orbiting scroll 22 that meshes with the fixed scroll 8 is provided, as in a normal scroll compressor. The orbiting scroll 22 has a generally disk-shaped end plate portion 22a, and a spiral blade portion 22 that axially protrudes from the end plate portion 22a and meshes with the spiral blade portion 8b of the fixed scroll 8 described above.
b. A cylindrical boss portion 22c projects in the axial direction from the back surface of the end plate portion 22a, and the boss portion 22c is rotatably supported by a bush 24 via a needle bearing 23. The bush 24 is attached to the eccentric shaft portion 2c that projects in the axial direction from the enlarged diameter portion 2b of the drive shaft 2. Reference numeral 25 is a rotation preventing mechanism 25 for the orbiting scroll 22.

In the scroll type compressor 1 of the first embodiment, a main bearing 26 that rotatably supports the enlarged diameter portion 2b of the drive shaft 2 is formed in a cup-like shape so as to project forward from the front housing 7. It is supported by the inner surface of the portion 7a. Therefore, the protruding portion 7a of the housing is
The rotor 20 of the electric motor 16, the field iron core 17, and the second housing 11 and the like cover the outside of the projecting portion 7a. Since the orbiting scroll 22 is cantilevered only by the main bearing 26, the enlarged diameter portion 2b of the drive shaft 2 and the main bearing 26 have large diameters, but the outer diameter of the protruding portion 7a of the housing is still the front housing. Since it is smaller than the outer diameter of 7, a useless space remains around the protrusion 7a. The scroll compressor 1 of the first embodiment is characterized in that the electric motor 16 is provided by utilizing this useless space around the main bearing 26.

Similar to a normal scroll compressor, a discharge port 27 is opened at the center of the end plate portion 8a of the fixed scroll 8, and a reed-shaped discharge valve 28 is provided in the rear housing 9.
From the side of the discharge chamber 29 formed as a space inside, the discharge port 2
Blocking 7. Further, inside the outer peripheral portion of the fixed scroll 8 which is a part of the housing, a suction chamber 30 as a space is formed on the outer periphery of the spiral blade portion 22b of the orbiting scroll 22.

Scroll compressor 1 in the illustrated embodiment
Is configured as a variable displacement compressor with variable discharge capacity. Therefore, the spiral blade 8b of the fixed scroll 8 and the spiral blade 22b of the orbiting scroll 22.
Fluid formed in pairs between and (refrigerant in this case)
Among the plurality of working chambers 31 for compressing the air, the one having a pressure intermediate between the low pressure one formed on the outer peripheral portion and the high pressure one formed near the central portion is communicated. In addition, at least one bypass port 32 is formed in the end plate portion 8a of the fixed scroll 8. Bypass port 32
Is closed by a reed-shaped bypass valve 34 from the side of the bypass chamber 33 formed as a space in the rear housing 9.

The bypass chamber 33 communicates with the suction chamber 30 via a bypass passage 33a formed in the rear housing 9 and a bypass passage 35 formed in the outer peripheral portion of the fixed scroll 8 in the axial direction. A control spool 36 is provided in the rear housing 9 as a valve body capable of blocking the communication between the bypass passage 33a and the bypass passage 35, and the spring 3 inserted in the bypass passage 35 is provided.
It is urged to the valve open position by 7. Spring 37
In order to press the control spool 36 toward the valve closing position against the biasing force of the control pressure chamber 3 in the rear housing 9.
8 is formed, and either high pressure (fluid pressure in the discharge chamber 29) or low pressure (fluid pressure in the suction chamber 30) is selectively guided by the control valve 39.

When a high pressure is supplied to the control pressure chamber 38 by the control valve 39, the control spool 36 is pressed to move to the valve closing position against the biasing force of the spring 37, and the bypass passage 33a and the bypass passage 33a. Cut off between 35. On the contrary, when the low pressure is supplied to the control pressure chamber 38, the control spool 36 is moved to the valve opening position by the spring 37, so that the bypass passages 33 a and 35 are communicated with each other and the high pressure and the low pressure are generated in the working chamber 31. As a result of returning a part of the fluid pressurized to an intermediate level to the suction chamber 30, the amount of the fluid discharged to the discharge chamber 29 decreases, and the capacity of the scroll compressor 1 decreases.

However, if the control valve 39 is duty-controlled, the pressure in the control pressure chamber 38 can be set to an intermediate pressure at an arbitrary height between the high pressure and the low pressure. It can be stopped at the position, and the amount of bypass from the bypass port 32 can be adjusted steplessly. As a result, the capacity of the scroll compressor 1 changes steplessly. In any case, the control valve 39 controls the amount of current supplied to the coil 18 when the electric motor 16 is driven,
It can be controlled by an electronic control unit (not shown) together with the intermittent operation of the current supplied to the coil 14 of the electromagnetic clutch 3.

Since the combined drive type scroll compressor 1 of the first embodiment is constructed in this way, when the compressor 1 is used as a refrigerant compressor of a vehicle air conditioner,
When the compressor 1 is driven by the vehicle running engine, the coil 14 of the electromagnetic clutch 3 is energized directly by a switch operated by the driver or automatically by an electronic control device. As a result, the iron core 15 is magnetized and the hub 4 made of a magnetic material is attracted.
The friction surface 4a of the pulley 6 and the friction surface 6a of the pulley 6 make frictional contact, and the power transmitted from the engine (not shown) to the pulley 6 via the belt is transmitted to the drive shaft 2 via the leaf spring 5. The orbiting scroll 22 tries to rotate as the eccentric shaft portion 2c of the drive shaft 2 rotates. Only revolve.

As a result, the spiral blade 8b of the fixed scroll 8 and the orbiting scroll 22 meshing with the blade 8b.
Working chamber 3 formed between the spiral-shaped blade portion 22b of
When 1 is opened toward the suction chamber 30 at the outer peripheral portion, the low-pressure refrigerant returning from the evaporator of the refrigeration cycle to the suction chamber 30 is taken into the working chamber 31. As the orbiting scroll 22 continues to revolve, the volume of the working chamber 31 is continuously reduced while the working chamber 31 at the outer peripheral portion is closed and moves toward the center portion, so that the refrigerant trapped in the working chamber 31 is closed. Is compressed. The pressurized refrigerant is discharged into the discharge chamber 29 by opening the discharge valve 28 from the discharge port 27 when the working chamber 31 is opened in the central portion. The high-pressure refrigerant in the discharge chamber 29 is sent from the discharge port 40 to the condenser of the refrigeration cycle.

When it becomes necessary to operate the vehicle air conditioner while the engine of the vehicle is stopped by, for example, idle stop, the driver operates the switch to
Alternatively, the coil 14 of the electromagnetic clutch 3 is automatically de-energized by the operation of the electronic control device, and the crankshaft of the engine and the drive shaft 2 of the compressor 1 are disconnected. When the electric power of the battery (not shown) is converted into electric power of three-phase AC by the inverter and supplied to the coil 18 of the electric motor 16 in that state, a rotating magnetic field is generated in the field iron core 17, so that the permanent magnet 21 follows it. Electric motor 1
The rotor 20 of 6 rotates, and the compressor 1 is rotationally driven via the drive shaft 2. Therefore, even when the engine is stopped, the compressor 1 can be driven by the electric power of the battery to operate the vehicle air conditioner.

Since the compound drive type scroll compressor 1 of the first embodiment is a variable displacement compressor, the control valve 39 is operated to change the pressure of the control pressure chamber 38 as described above. When the control spool 36 is in the valve open position, part of the refrigerant that has been partially pressurized is bypass passage 33.
Since it returns to the suction chamber 30 through a and 35, the amount of the refrigerant discharged to the discharge chamber 29 and circulating in the refrigeration cycle decreases,
The cooling capacity of the air conditioner is reduced. However, compressor 1
Is rotationally driven by the electric motor 16, the rotational speed of the drive shaft 2 is changed by changing the amount of current supplied to the coil 18 of the electric motor 16 to efficiently discharge the compressor 1 per unit time. It is not necessary to change the capacity of the compressor 1 by bypass because it can be adjusted.

In any case, in the combined drive type scroll compressor 1 of the first embodiment, the electric motor 16 is provided by utilizing the space around the main bearing 26, which should be called a dead space, so that the compression is performed. By attaching the electric motor 16 to the machine 1, the outer diameter and the axial length do not increase as a whole. Further, in this case, the pulley 6 is provided with the electromagnetic clutch 3 therein, but since the outer diameter of the electromagnetic clutch 3 is not so large, the diameter of the pulley 6 does not become excessively large and the compressor 1 is compact. Even when the required discharge amount of the refrigerant is obtained by increasing the speed to drive the engine, it is not necessary to increase the diameter of the drive-side pulley attached to the crankshaft of the engine. Therefore, the belt transmission device and the compressor 1 are increased in size. You don't have to. Therefore, the compressor 1 can be easily installed in a small vehicle having a small space.

FIG. 2 shows, as a second embodiment of the composite drive type compressor of the present invention, the front housing 7 and the second housing 1 in the composite drive type scroll compressor 1 of the first embodiment.
1 shows a cross-sectional structure of a compound drive type scroll compressor 41 in which the shape and structure of No. 1 are changed. The same components as those of the compressor 1 of the first embodiment are designated by the same reference numerals, and the overlapping detailed description will be omitted.

The characteristic of the compressor 41 of the second embodiment with respect to the compressor 1 of the first embodiment is that the field core 17 of the electric motor 16 is
In the first embodiment, it is attached to the inner surface of the second housing 11 attached to the front of the front housing 7, whereas in the second embodiment, it is integrally attached to the front end of the outer periphery of the front housing 7. That is, the stator support portion 7b extending forward is provided and attached to the inner surface thereof. Therefore, the second housing 11a becomes smaller by the amount of the newly installed stator support portion 7b, and supports only the electromagnetic clutch 3 and the pulley 6. As described above, the compressor 41 of the second embodiment is partially different in shape and structure from the compressor 1 of the first embodiment, but is functionally the same as that of the first embodiment.

FIG. 3 shows a sectional structure of a compound drive type scroll compressor 42 as a third embodiment of the present invention. Also in this case, the same components as those of the compressor 1 of the first embodiment are designated by the same reference numerals, and the overlapping detailed description will be omitted. A feature of the compressor 42 of the third embodiment with respect to the compressor 1 of the first embodiment is that the positions of the outer stator and the inner rotor are interchanged. That is, in the compressor 42 of the third embodiment, the field iron core 17 is attached to the outer surface of the projecting portion 7a of the front housing 7, and the plurality of permanent magnets 21 are attached to the inner surface of the rotor 20. There is. Therefore, the compressor 42 of the third embodiment
The second housing 11 at supports only the electromagnetic clutch 3 and the pulley 6.

As described above, in the third embodiment, even if the positional relationship between the field iron core 17 and the permanent magnet 21 is switched inside and outside, there is no difference in operation and effect from the first embodiment.

In each of the first to third embodiments, an electromagnetic clutch 3 is attached to the drive shaft 2, but these compressors 1, 41, 42 are variable displacement compressors. So, if there is a means to these compressors that makes it possible to bring the capacity to a small value at or near 0%,
By adding means for preventing the drive shaft 2 from driving the pulley 6 in the reverse direction, it is not necessary to provide the electromagnetic clutch 3 or the like. The compound drive type scroll type compressor 43 of the fourth embodiment shown in FIG. 4 has the same main body part as that of the compressor 1 of the first embodiment, but means for making the capacity of the compressor 0%. By adding a one-way clutch 44 having a simple structure such as a freewheel which becomes idle when the pulley 6 is driven from the drive shaft 2, the relatively expensive electromagnetic clutch 3 is omitted and the pulley 6 is replaced. It shows an example in which the internal structure is simplified.

In the combined drive type scroll compressor 43 of the fourth embodiment, similar to the compressor 1 of the first embodiment, the bypass opened and closed by the control spool 36 between the bypass chamber 33 and the bypass passage 35. By providing the passage 33a,
Not only is it possible to extract a part of the uncompressed fluid from the working chamber 31 via the bypass port 32 and allow it to flow out to the suction chamber 30, but also a discharge chamber 29 through which a high-pressure fluid passes. A bypass passage 29a is also provided so that the discharge chamber 29 communicates with the bypass passage 35 through the bypass passage 29a when the control spool 36 is in the fully open position at the right end. By returning almost all the amount to the suction chamber 30, the capacity of the compressor 43 becomes 0%.

Therefore, by controlling the duty of the control valve 39, the pressure of the control pressure chamber 38 is set to an arbitrary height between the pressures of the suction chamber 30 and the discharge chamber 29, and the spring 37 is set.
When the control spool 36 is moved to an arbitrary half-open position by the urging force of the bypass passage 33a, the bypass passage 33a is closed.
5, a part of the fluid in the working chamber 31 pushes open the bypass valve 34, flows out from the bypass port 32 to the bypass chamber 33, and returns to the suction chamber 30 through the bypass passage 33a and the bypass passage 35. Therefore, the capacity of the compressor 43 of the fourth embodiment is reduced to an arbitrary height. Further, if the pressure in the control pressure chamber 38 is set to the minimum pressure (suction pressure) by the control valve 39, the control spool 36 moves to the fully open position at the right end, and as a result, almost all of the high-pressure fluid in the discharge chamber 29 is sucked. Returning to the chamber 30, the capacity of the compressor 43 becomes substantially 0%, so there is no need to provide an electromagnetic clutch or the like on the pulley 6 to cut off the power. Thus, the operation of reducing the capacity of the compressor 43 to 0% is effective when the compressor 43 is driven by a main power source such as a vehicle running engine.

Since the engine is stopped when the compressor 43 of the fourth embodiment is driven by the electric motor 16 which is the secondary power source, the drive shaft 2 is the boss portion 45 of the pulley 6.
, The one-way clutch 44 is provided between the drive shaft 2 and the boss portion 45, and the one-way clutch 44 idles in the reverse drive state.
It is prevented that 6 drives the engine in reverse. Note that the capacity can be controlled by the control valve 39 even when the compressor 43 is driven by the electric motor 16. In this case, the frequency of the three-phase AC power supplied to the coil 18 of the electric motor 16 is controlled by an electronic control device or the like. It is better to control the discharge amount of the compressor 43 per unit time by changing the number of rotations of the drive shaft 2 by controlling.

Thus, in the scroll type compressor 43 of the fourth embodiment, as in the above-described respective embodiments, the size of the compressor is reduced by disposing the electric motor 16 in the dead space of the outer peripheral portion of the main bearing 26. In addition to the common effect of the present invention, that is, the effect of reducing the cost by omitting the electromagnetic clutch 3 and the effect that stepless control of the discharge capacity becomes possible are achieved.

In each of the first to fourth embodiments, the drive shaft 2 is pivotally supported by a single main bearing 26, but the drive shaft 2 may be pivotally supported by a plurality of bearings. It is possible. The structure is illustrated in FIG. 5 as the fifth embodiment. In the compound drive type scroll compressor 46 of the fifth embodiment, in addition to the main bearing 26, a portion near the shaft end of the drive shaft 2 is axially supported by an auxiliary bearing 47. In this case, the auxiliary bearing 47 is supported by the tip portion of the second housing 11 as with the pulley 6 and the electromagnetic clutch 3. The main bearing 26 is similar to each of the above-described embodiments.
It is supported by the protruding portion 7 a of the front housing 7. Since the shaft seal device 48 is provided between the two bearings 26 and 47, the auxiliary bearing 47 is not exposed to a fluid such as a refrigerant compressed by the compressor 46. Further, since the load of the main bearing 26 is reduced by providing the auxiliary bearing 47, it is possible to make it small. Incidentally, the compressor 46 of the fifth embodiment also
It is of a variable capacitance type as in the above-described examples, but the mechanism for changing the capacitance is not shown.

In the above description of the embodiments, all of the compressors taken up belong to the scroll type compressor, but the main object of the present invention is to provide the electric motor 16 on the outer peripheral portion of the main bearing 26. Since the entire compressor is miniaturized by the above, the same position as that of the main bearing 26 of each embodiment is applied to a compressor other than the scroll compressor, for example, a swash plate type variable capacity compressor. When the bearing is provided, the same effect as the above case can be obtained by providing the electric motor by utilizing the dead space of the outer peripheral portion of the bearing.

Further, in the above description of the embodiments, each compound drive type compressor has an internal combustion engine (engine) as a main power source mounted on a vehicle for traveling and a compression as a secondary power source. Although it is described as being driven by either one of the electric motors 16 integrated with the main body of the machine, it is also possible to simultaneously operate the two power sources to drive the compressor at the same time, if necessary. is there.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing a first embodiment of a compound drive type compressor of the present invention.

FIG. 2 is a vertical cross-sectional view showing a second embodiment of the compound drive type compressor of the present invention.

FIG. 3 is a longitudinal sectional view showing a third embodiment of the compound drive type compressor of the present invention.

FIG. 4 is a vertical sectional view showing a fourth embodiment of the compound drive type compressor of the present invention.

FIG. 5 is a vertical sectional view showing a fifth embodiment of the compound drive type compressor of the present invention.

[Explanation of symbols]

1 ... Composite drive type scroll compressor of the first embodiment 2 ... Drive shaft 3 ... Electromagnetic clutch 6 ... Pulley 16 ... Electric motor 26 ... Main bearing 29 ... Discharge chamber 30 ... Inhalation chamber 32 ... Bypass port 33 ... Bypass room 35 ... Bypass passage 36 ... Control spool 38 ... Control pressure chamber 39 ... Control valve 41 ... Composite drive type scroll compressor of the second embodiment 42 ... Combined drive type scroll compressor of the third embodiment 43 ... Composite drive type scroll compressor of the fourth embodiment 44 ... One-way clutch 46 ... Composite drive type scroll compressor of the fifth embodiment 47 ... Auxiliary bearing 48 ... Shaft sealing device

Claims (11)

[Claims] 1. A composite drive type compressor that can be rotationally driven by a plurality of power sources at the same time or selectively by any one of them, and is common to the plurality of power sources. Utilizing a drive shaft, a bearing for supporting the drive shaft, an input means attached to the drive shaft for receiving power from one power source, and a dead space formed on an outer peripheral portion of the bearing. A composite drive compressor, which is configured and further includes an electric motor which is connected to the drive shaft and serves as another power source. 2. The combined drive type compressor according to claim 1, wherein the one power source is an internal combustion engine mounted on a vehicle. 3. The compressor according to claim 1, wherein the main body of the compressor, the electric motor formed on the outer peripheral portion of the bearing, and the input means are sequentially arranged in the axial direction of the drive shaft. Combined drive type compressor. 4. The method according to any one of claims 1 to 3,
A composite drive compressor, wherein the input means attached to the drive shaft for one power source is a pulley attached to one end of the drive shaft for a transmission belt. 5. The method according to any one of claims 1 to 4,
A compound drive compressor wherein the input means mounted to the drive shaft for one power source includes an electromagnetic clutch. 6. The method according to any one of claims 1 to 5,
A compound drive type compressor characterized in that the compressor is of a variable capacity type. 7. The compressor of claim 6, wherein the compressor is capable of operating at 0% capacity and the input means mounted to the drive shaft for one power source includes a one-way clutch. The compound drive type compressor characterized in that 8. The method according to claim 1, wherein
A compound drive type compressor characterized in that the compressor body is a scroll type compressor. 9. The scroll housing according to claim 8, wherein a second housing integrated with a housing on the compressor body side is supported on an outer peripheral portion of the bearing that supports the drive shaft of the compressor body. And the pulley is rotatably supported by the tip portion of the second housing. 10. The electric motor according to claim 8, wherein an outer peripheral portion of the bearing that supports the drive shaft of the scroll-type compressor body is supported by a part of a housing on the compressor body side. Is configured,
A compound drive compressor, wherein the pulley is rotatably supported by a second housing integrated with a housing on the compressor body side. 11. The bearing according to claim 8, wherein a plurality of bearings for supporting the drive shaft of the scroll-type compressor body are provided, and the electric motor is formed on at least one outer peripheral portion of the bearings. The compound drive type compressor characterized in that