Composite drive system for compressor

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a composite drive system, for a compressor, capable of rotationally driving the compressor selectively or at the same time by either of two drive sources including a prime mover such as an internal combustion engine and a motor rotated by the power of a battery.

2. Description of the Related Art

To cope with the environmental problems in recent years, the practical application of an idle-stop (or “eco-run”) system has been promoted for stopping an internal combustion engine when a vehicle such as an automobile, with the engine mounted thereon, has stopped. When this system is used, as long as the vehicle is stationary, the compressor of the air-conditioning system of the particular vehicle also stops and the air-conditioning system is turned off, thereby causing the vehicle occupants to feel uncomfortable. In view of this, a “hybrid compressor” is known which can be driven by either of two drive sources. Specifically, while the vehicle is stationary, the drive source is switched from the internal combustion engine to a motor rotationally driven by the power stored in a battery thereby to drive a compressor.

As a first well-known example of the hybrid compressor, a system capable of driving a swash-plate compressor selectively by one of two drive sources, including an internal combustion engine and a battery, has been proposed. In this system, a pulley having an electromagnetic clutch widely used for an automotive air-conditioning system is mounted on the drive shaft of a swash-plate compressor with the discharge amount thereof variable for each rotation. This pulley is adapted to be rotationally driven by the internal combustion engine through a belt. On the other hand, a motor driven by battery power is mounted on the drive shaft of the same compressor. In the normal operating mode of this system, the compressor is driven by the internal combustion engine, and when it is foreseen that the time has come to stop the engine or switch the drive source of the compressor from the engine to the motor, the angle of inclination of the swash plate of the compressor, changing with the magnitude of the cooling load, is detected. In the case where the inclination angle is large, indicating that the cooling load is heavy, the deenergization of the electromagnetic clutch and the stopping of the internal combustion engine are delayed. Thus, the compressor continues to be driven by the internal combustion engine. In the case where the cooling load is light and, therefore, the inclination angle of the swash plate is small, on the other hand, the electromagnetic clutch is immediately deenergized while at the same time stopping the internal combustion engine. Thus, the compressor is driven by the motor.

In a second well-known example of the hybrid compressor described in Japanese Unexamined Utility Model Publication No. 6-87678, as in the first well-known example, the drive shaft of the swash-plate compressor is rotationally driven selectively by two drive sources, i.e. by an internal combustion engine connected to the drive shaft of the swash-plate compressor through a belt, a pulley and an electromagnetic clutch, or by a motor driven by the battery directly and connected with the drive shaft of the compressor. The feature of this conventional hybrid compressor lies in that, while the compressor is driven by the internal combustion engine, the same motor is used as a generator from which power is acquired and stored in a battery.

The first well-known example of the hybrid compressor poses the problems that a swash-plate compressor of a variable displacement type having a complicated structure is used to make the discharge capacity variable, that the motor is only an auxiliary drive source for driving the compressor temporarily while the internal combustion engine is out of operation and is useless in other points, that a complicated control operation is required in spite of the rather poor functions and effects, and that the pulley for receiving the power from the internal combustion engine is very bulky because the electromagnetic clutch and the motor are built inside of the pulley.

On the other hand, the problems of the second well-known example of the hybrid compressor are that a swash-plate compressor of a variable displacement type having a complicated structure is used to make the discharge capacity variable, and that an electromagnetic clutch and a motor are built inside the pulley in radially superposed positions and therefore the pulley is bulkier than that of the first well-known example of the hybrid compressor. In the second well-known example, however, the motor is used also as a generator. Therefore, although this motor is not a simple auxiliary drive source used selectively in coordination with the internal combustion engine, the additional function of the motor for power generation is undesirably overlapped with the operation of the generator for charging the battery always attached to the internal combustion engine. Also, the motor for power generation is not used in other than the season when the cooling system is operated, and therefore the generator attached to the internal combustion engine cannot be eliminated and replaced by the motor. Thus, the use of the motor for driving the compressor as a generator leads to no special advantage. Both of the conventional hybrid compressors described above, therefore, have no greater advantage than the basic functions and effects of selectively using two drive sources at the sacrifice of a complicated compressor structure and the resulting considerably increased volume of the compressor and the related component parts.

SUMMARY OF THE INVENTION

An object of the present invention is obviate the above-mentioned problems of the prior art and to provide an improved compact, lightweight composite drive system for a compressor which can be fabricated at low cost and has such a novel configuration that the discharge capacity per unit time can be changed over a wide range even when using a fixed displacement compressor of a simple structure having a predetermined discharge capacity per rotation instead of a variable displacement compressor having a complicated structure with an electromagnetic clutch.

Another object of the invention is to provide an improved composite drive system for a compressor, in which an electromagnetic clutch is not required even in the case where a variable displacement compressor is used and in which the whole system including the compressor and the input means receiving power from the prime mover and the motor for driving the compressor has a smaller size and weight than the conventional hybrid compressor.

According to one aspect of the invention, there is provided a composite drive system for a compressor which obviates the aforementioned various problems of the prior art in the manner described below (claim

1

).

The composite drive system according to this aspect of the invention uses a dynamo-electric machine (hereinafter referred to as “the dynamotor”) capable of operating both as a motor and as a generator and including a rotatable field portion and a rotatable armature portion, wherein a selected one of the armature portion and the field portion of the dynamotor is operatively interlocked with the output shaft of the prime mover, while the other one of the armature portion and the field portion is operatively interlocked with the drive shaft of the compressor. The dynamotor is connected with a power supply unit such as a battery through a power control unit.

In the case where the dynamotor is operated in motor mode by the power control unit, the turning effort of the output shaft of the prime mover received by selected one of the armature portion and the field portion of the dynamotor is output from the other one of the armature portion and the field portion as a turning effort having a higher rotational speed by adding the rotational speed generated between the armature portion and the field portion, as a motor, to the rotational speed received, so that the drive shaft of the compressor is driven by the particular turning effort. As a result, the discharge capacity per unit time of even a compact, lightweight compressor of fixed displacement type having a small discharge capacity per rotation can be freely controlled either upward or downward. In addition, when the prime mover is stationary, the compressor can be driven only by the dynamotor and the power supply unit, and in the case where the dynamotor is set in unloaded operation mode by disconnecting the dynamotor and the power supply unit, by the power control unit, the compressor can be stopped without using the electromagnetic clutch while the prime mover is in operation.

Further, in the event that the output rotational speed of the prime mover is excessively increased, the dynamotor is operated in generator mode by the power control unit, and by thus recovering the generated power to the power supply unit, the turning effort of the output shaft of the prime mover received from a selected one of the armature portion and the field portion of the dynamotor is partially converted into power and stored in the power supply unit. As a result, a reduced rotational speed is output from the other one of the armature portion and the field portion by adding the negative rotational speed generated between the armature portion and the field portion as a generator to the rotational speed received, so that the drive shaft of the compressor is driven by the motive power with an arbitrarily reduced rotational speed.

In this way, the wasteful consumption of energy is eliminated on the one hand and, even in the case where the rotational speed of the prime mover is excessively increased for the compressor of fixed displacement type, the discharge capacity per unit time of an arbitrary magnitude required of the compressor can be secured by freely controlling the rotational speed of the compressor on the other hand. Also, in the case where the power supply unit has no margin for receiving the power from the dynamotor, the rotational speed of the compressor can be regulated at the desired level, for example, by performing the duty factor control operation for switching between the unloaded operation mode and the generator mode at short time intervals.

According to another aspect of the invention, there is provided a composite drive system for a compressor which obviates the aforementioned various problems of the prior art in the manner described below (claim

6

).

The composite drive system according to this aspect of the invention comprises a dynamotor capable of operating both as a motor and as a generator, and including a rotor having a plurality of permanent magnets on the peripheral surface thereof and an iron core having a plurality of coils and fixed at a position in opposed relation to the rotor. The dynamotor is connected to a power supply unit like a battery through a power control unit. A one-way clutch can be interposed between the rotor of the dynamotor and the input means receiving power from a prime mover constituting a main drive source.

In this dynamotor, the rotor is kept rotated as long as the prime mover constituting the main drive source such as an internal combustion engine is in operation. Therefore, the dynamotor is kept in generator mode and can always generate power as a generator, except when it is used in motor mode for driving the compressor in place of the main prime mover. This power is stored in the power supply unit through the power control unit. Even in the season when the compressor is not operated, therefore, the dynamotor operates as a generator.

A specific embodiment of the invention is the internal combustion engine mounted on a vehicle as a preferred prime mover. The compressor can be suitably used as a refrigerant compressor of an air-conditioning system of a vehicle. The battery mounted on the vehicle can be used as a power supply unit. In such a case, even when the internal combustion engine is stationary under idle-stop control, the air-conditioning system can be operated by driving the compressor using the dynamotor and the battery.

The use of the dynamotor of magnet type having at least a permanent magnet simplifies the structure, and therefore makes it possible to manufacture a compact, lightweight dynamotor at a lower cost. This is also true in the case where the dynamotor is incorporated in a driven pulley on the side of the compressor rotationally driven through a belt by the output shaft of a prime mover such as an internal combustion engine. In any case, the whole configuration of the composite drive system for the compressor can be reduced in size and weight, and can be easily built in a limited space such as the engine compartment of a vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other objects, features and advantages will be made apparent by the detailed description taken in conjunction with the accompanying drawings, in which:

FIG. 1

is a longitudinal sectional view showing the essential parts of a first embodiment of the invention;

FIG. 2

is a cross sectional view showing the essential parts taken in line II—II in

FIG. 1

;

FIG. 3

includes connection diagrams (

a

) to (

d

) each for illustrating a method of connecting a plurality of coils of a three-phase AC dynamotor;

FIG. 4

is a schematic diagram illustrating a general configuration of a composite drive system for a compressor according to the invention;

FIG. 5

is a diagram for explaining the operation of the dynamotor according to the invention;

FIG. 6

is a time chart for explaining the duty factor control operation according to the invention;

FIG. 7

is a longitudinal sectional view showing the essential parts according to a second embodiment of the invention;

FIG. 8

is a longitudinal sectional view showing the essential parts according to a third embodiment of the invention;

FIG. 9

is a cross sectional view of the essential parts taken in line IX—IX in

FIG. 8

;

FIG. 10

is a longitudinal sectional view showing the essential parts according to a fourth embodiment of the invention;

FIG. 11

is a circuit diagram illustrating the contents of a power control unit used for a DC dynamotor;

FIG. 12

is a circuit diagram illustrating the contents of a power control unit used for a three-phase AC dynamotor;

FIG. 13

is a longitudinal sectional view showing the essential parts according to a fifth embodiment of the invention;

FIG. 14

is a cross sectional view of the essential parts taken in line XIV—XIV in

FIG. 13

;

FIG. 15

is a longitudinal sectional view showing the essential parts according to a sixth embodiment of the invention;

FIG. 16

is a longitudinal sectional view showing the essential parts according to a seventh embodiment of the invention;

FIG. 17

is a longitudinal sectional view showing the essential parts according to an eighth embodiment of the invention;

FIG. 18

is a longitudinal sectional view showing the essential parts according to a ninth embodiment of the invention;

FIG. 19

is a longitudinal sectional view showing the essential parts according to a tenth embodiment of the invention; and

FIG. 20

is a longitudinal sectional view showing the essential parts according to an 11th embodiment of the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

A composite drive system for a compressor according to a first embodiment of the invention will be explained with reference to

FIGS. 1

to

6

. As is apparent from

FIG. 1

, showing a longitudinal sectional view of the essential parts, a compressor

1

to be driven by the system is a scroll compressor having a well-known structure. Especially, this embodiment employs a compressor of fixed displacement type having no mechanism therein for changing the discharge capacity per rotation. The compressor

1

may be of a type other than a scroll compressor. The structure and operation of the scroll compressor are well known, and therefore will not be explained below. In short, the compressor

1

has a single drive shaft

2

for receiving the motive power and, when the drive shaft

2

is rotationally driven, it can compress a fluid such as a refrigerant circulated through the refrigeration cycle of an automotive air-conditioning system.

The discharge capacity per rotation of the compressor

1

may be normally about one half or one third of the normal discharge capacity. This is by reason of the fact that the composite drive system according to this invention can drive the compressor

1

at a higher speed than the rotational speed of the internal combustion engine, and therefore, even in the case where the discharge capacity per rotation is small as compared with that for the compressor driven only by the internal combustion engine, the discharge capacity per unit time is sufficiently large. The compressor

1

is of fixed displacement type and has a small discharge capacity per rotation, so that the size of the compressor

1

can be reduced remarkably as compared with the normal variable displacement compressor.

A substantially cylindrical housing

4

of a dynamotor

3

capable of operating both as a motor and as a generator is integrated with a housing la of the compressor

1

. Reference numeral

5

designates a disk-shaped end plate for closing the front end of the housing

4

of the dynamotor

3

. The disk-shaped end plate

5

is fastened to the housing

4

by a bolt or the like not shown. The drive shaft

2

of the compressor

1

extends into the internal space of the housing

4

of the dynamotor

3

, and is mounted on the bottom surface

6

a

of a cup-shaped field portion

6

of the dynamotor

3

. The field portion

5

is made of a magnetic material such as cast steel and is rotatably supported on a bearing

8

for supporting the bearing

7

in the housing

4

and the drive shaft

2

of the compressor

1

. In this way, the field portion

6

of the dynamotor

3

has the feature that it can be rotated with respect to the fixed housing

4

unlike the normal motor or generator. This feature is not limited to the first embodiment but constitutes one of the basic features of the configuration according to the present invention. In

FIG. 1

, numeral

9

designates a shaft seal unit for hermetically sealing the internal space of the compressor

1

against the internal space of the dynamotor

3

.

As is apparent, from not only

FIG. 1

but also from

FIG. 2

showing a cross sectional view taken in line II—II in

FIG. 1

, four permanent magnets

10

are mounted on the cylindrical inner surface of the field portion

6

of the dynamotor

3

in such positions as to divide the circumference into equal parts. A cylindrical field surface

10

a

is substantially formed by the inner surfaces of the four permanent magnets

10

. The permanent magnets

10

according to the shown embodiment are each magnetized in the direction along the thickness (radial direction) thereof. Therefore, the N and S poles of the permanent magnets

10

are arranged along the circumference of the field surface

10

a

in such a manner that adjacent ones of the permanent magnets

10

are magnetized in opposite directions. However, this embodiment is not intended to limit the number, the direction of magnetization or the arrangement of the permanent magnets

10

, for which an ordinary technique for the magnet motor or the magnet generator can be employed.

The rotary shaft

11

of the dynamotor

3

is rotatably supported by the bearing

12

arranged on the bottom surface

6

a

of the field portion

6

and the bearing

13

arranged at the end plate

5

of the housing

4

in such a manner as to coincide with the center axis of the field portion

6

. As shown in

FIG. 2

, an iron core

14

having six radial protrusions at equal intervals are mounted on the rotary shaft

11

in such a manner as to form a slight gap with the field surface

10

a

of the permanent magnets

10

. In this way, the iron core

14

can rotate with the rotary shaft

11

independently of the rotatable field portion

6

. Each of the radial protrusions of the iron core

14

is wound with a coil

15

.

Three slip rings

16

are mounted on the rotary shaft

11

through an insulating member. Brushes

17

mounted on the end plate

5

of the housing

4

through the insulating member are kept elastically in sliding contact with the slip rings

16

, respectively. One end and the other end of each of the six coils

15

a

to

15

f

are connected to one of the slip rings

16

a

to

16

c

or one end or the other end of an adjacent one of the coils

15

a

to

15

f

in a predetermined manner. Four methods of connection are illustrated in (

a

) to (

d

) of FIG.

3

. For actual practice of these connection methods, a well-known technique for an approximate dynamotor (a motor or a generator with the field portion fixed) can be referred to. In this specification, the iron core

14

, the coil

15

, etc. rotatable with the rotary shaft

11

are collectively called an armature portion

18

as against the rotatable field portion

6

.

FIG. 4

is a diagram schematically showing a general configuration of the composite drive system for the compressor according to a first embodiment. A pulley (input means)

19

mounted on the front end of the rotary shaft

11

of the dynamotor

3

is operatively interlocked with a mating pulley

21

through a belt

20

. The pulley

21

is mounted on the output shaft

23

such as the crankshaft of an internal combustion engine (a prime mover in general terms)

22

mounted as a main drive source on the vehicle. Numeral

24

designates a power supply unit such as a battery mounted on the vehicle. As described later, the power supply unit

24

can supply power to the dynamotor

3

when the dynamotor

3

operates as a motor in motor mode, while the power supply unit

24

can receive and store power from the dynamotor

3

when the dynamotor

3

operates as a generator in generator mode. The battery

24

is charged also by another generator, not shown, rotationally driven by the internal combustion engine

22

. As long as the dynamotor

3

can supply a sufficient amount of power, however, the dynamotor

3

can act as a main generator for the vehicle.

Various control operations are required. They include the switching of the two operating modes, i.e. the motor mode and the generator mode of the dynamotor

3

, the conversion or rectification between the DC power and the three-phase AC power, and the circuit disconnection for cutting off the current flow between the dynamotor

3

and the battery

24

. In view of these needs, a power control unit,

25

including a computer and an electrical circuit for executing commands from the computer, is interposed between the battery

24

and the dynamotor

3

. Example configurations of the power control unit

25

will be specifically explained later.

According to the first embodiment, when the dynamotor

3

is set in motor mode by the power control unit

25

, the DC power supplied from the battery

24

is converted by the power control unit

25

into the three-phase AC power and supplied to the three brushes

17

of the dynamotor

3

. In the case where the dynamotor

3

is set in generator mode, in contrast, the three-phase AC power generated by the rotational drive of the dynamotor

3

is rectified by the power control unit

25

and supplied as DC power to the battery

24

and stored in the battery

24

together with the power generated by the generator normally incorporated in the internal combustion engine

22

. In the case where the compressor

1

is used as a refrigerant compressor in the refrigeration cycle of the automotive air-conditioning system, for example, the above-mentioned operation of the power control unit

25

is automatically started upon turning on of the operating switch of the automotive air-conditioning system.

The composite drive system for the compressor

1

according to the first embodiment is configured as described above. As long as the internal combustion engine

22

is in operation, therefore, the turning effort thereof is transmitted to the output shaft

23

, the pulley

21

, the belt

20

and the pulley

19

, in that order, thereby to rotate the rotary shaft

11

and the armature portion

18

of the dynamotor

3

shown in FIG.

1

. In the case where no current flows between the power control unit

25

and the dynamotor

3

under this condition, the iron core of the armature portion

18

having the coils

15

is not magnetized, and therefore substantially fails to apply the force to the field portion

6

having the permanent magnets

10

. Thus the armature portion

18

is simply activated in unloaded state, while the field portion

6

and the drive shaft

2

of the compressor

1

are not rotated. Taking advantage of this operation of the dynamotor

3

in an unloaded mode, the electromagnetic clutch for deactivating the compressor

1

when the air-conditioning system is not required and can be eliminated in the case where the compressor

1

is used as a refrigerant compressor of the air-conditioning system. As a result, the composite drive system can be reduced in size and weight and can be manufactured at a lower cost.

For operating the air-conditioning system, the compressor

1

is activated, in which case the power control unit

25

switches the dynamotor

3

to motor mode. As described later, the power control unit

25

includes a computer for issuing control commands and a circuit for executing the commands. This circuit has the function of a switch, the function of an inverter and the function of a rectifier. Once the computer designates the operation in motor mode, therefore, the power control unit

25

converts the DC power of the battery

24

into the three-phase AC power and supplies it to the brushes

17

of the dynamotor

3

. This power is supplied to the coils

15

of the armature portion

18

through the slip rings

16

, and therefore a rotary magnetic field is formed around the rotary shaft

11

on the armature portion

18

. As a result, the field portion

6

having the permanent magnets

10

and the armature portion

18

that has generated the rotary magnetic field rotate relatively to each other for generating the attracting force and the repulsive force in the direction along the circumference (along the tangential direction), so that the dynamotor

3

operates as a motor. According to the first embodiment, the output of the dynamotor

3

as a motor is produced from the field portion

6

in rotation. Thus, the turning effort of the field portion

6

is transmitted to the compressor

1

through the drive shaft

2

, so that the compressor

1

compresses a refrigerant or the like fluid.

According to the first embodiment, the rotary shaft

11

and the armature portion

18

of the dynamotor

3

are rotationally driven by the internal combustion engine

22

through the pulley

19

, and the field portion

6

of the dynamotor

3

operating as a motor is rotated, at a higher speed than the armature portion

18

, with the aid of the armature portion

18

. If the difference between the rotational speed on the output side less the rotational speed on the input side of the dynamotor

3

, i.e. the relative rotational speed between the armature portion

18

and the field portion

6

, which is a rotational speed derived from the dynamotor

3

alone, is defined as “the rotational speed ΔN of the dynamotor

3

” then, as long as the dynamotor

3

is operating in motor mode, ΔN assumes a positive value. In this case, as a matter of course, the rotational speed of the drive shaft

2

constituting the rotational speed of the compressor

1

is given as the sum of the rotational speed of the rotary shaft

11

(i.e. the rotational speed of the pulley

19

) and the rotational speed ΔN of the dynamotor

3

.

The value of this sum is, of course, changed steplessly even in the case where the rotational speed of the rotary shaft

11

is changed with the change of the rotational speed of the internal combustion engine

22

or even in the case where the rotational speed ΔN of the dynamotor

3

is changed by controlling the three-phase AC electric energy supplied to the dynamotor

3

. In the case of a vehicle, the rotational speed of the internal combustion engine

22

changes in accordance with the vehicle running condition, and the rotational speed of the internal combustion engine

22

cannot, generally, be changed for the sole purpose of controlling the air-conditioning system. For changing the cooling capacity of the air-conditioning system, therefore, the rotational speed ΔN of the dynamotor

3

must be changed.

The dynamotor

3

according to the first embodiment is of three-phase AC type. For changing the rotational speed ΔN of the dynamotor

3

, therefore, the frequency of the three-phase AC power supplied is changed under the control of the power control unit

25

. As a result, the rotational speed of the rotary magnetic field of the armature portion

18

changes and so does the value of ΔN. The magnitude of the torque generated by the dynamotor

3

operating as a motor is changed also in the case where the current amount is changed by changing the voltage applied to the dynamotor

3

and thus changing the electric energy supplied, while at the same time maintaining the frequency of the three-phase AC power supply constant. As related to the magnitude of the load torque of the compressor

1

changing in accordance with the cooling load of the air-conditioning system, therefore, the slip rate of the dynamotor

3

, i.e. the degree to which the rotation of the field portion

6

is delayed with respect to the rotation of the rotary magnetic field of the armature portion

18

is changed thereby to change ΔN, resulting in the change in the rotational speed of the drive shaft

2

of the compressor

1

. It is thus possible to control the rotational speed of the drive shaft

2

also by this method.

As described above, in the case where the dynamotor

3

is set in motor mode by the power control unit

25

, the rotational speed ΔN of the dynamotor

3

defined above is added to the rotational speed of the pulley

19

due to the internal combustion engine, and therefore the rotational speed of the drive shaft

2

is increased beyond the rotational speed of the pulley

19

. Even in the case where the discharge capacity per rotation of the compressor

1

is small, therefore, the discharge capacity per unit time is increased due to the high rotational speed. Even the use of the compressor

1

smaller in size and weight than the conventional compressor and having a discharge capacity per rotation as small as one half or one third that of the conventional compressor can secure the required discharge capacity per unit time. Also, the discharge capacity per unit time of the compressor

1

and the cooling capacity of the air-conditioning system can be changed steplessly by controlling the frequency or the electric energy of the power supplied to the dynamotor

3

by the power control unit

25

and thereby changing the rotational speed ΔN of the dynamotor

3

.

As apparent from the foregoing description, the discharge capacity per unit time of the compressor

1

and hence the cooling capacity of the air-conditioning system can be calculated as follows:

Discharge capacity per unit time=(rotational speed of rotary shaft

11

+rotational speed ΔN of dynamotor

3

)×(discharge capacity per rotation of compressor

1

)

Also in the case where the air-conditioning system is operated only with the power of the battery

24

when the internal combustion engine

22

is stopped by idle-stop control, for example, the power control unit

25

selects the motor mode for the dynamotor

3

. In this case, the pulley

19

and the rotary shaft

11

are stopped with the internal combustion engine

22

, and therefore the rotational speed ΔN of the dynamotor

3

itself constitutes the rotational speed of the drive shaft

2

of the compressor

1

. Also in this case, the cooling capacity of the air-conditioning system can be adjusted to an arbitrary level by changing the frequency of the three-phase AC power supplied to the dynamotor

3

and thus changing the rotational speed of the drive shaft

2

freely and under the control of the power control unit

25

.

As is apparent from the foregoing description, with the composite drive system according to the invention, the rotational speed ΔN of the dynamotor

3

is added to the rotational speed of the pulley

19

(rotary shaft

11

) driven by the internal combustion engine

22

when the dynamotor

3

is in motor mode. Therefore, the rotational speed of the drive shaft

2

of the compressor

1

is higher than in the prior art in which the compressor is driven by the internal combustion engine alone. In the case where the discharge capacity of the compressor

1

becomes excessively high and exceeds the required discharge capacity of the compressor

1

, therefore, the generator mode is selected by the power control unit

25

. By thus operating the dynamotor

3

as a generator, the discharge capacity of the compressor

1

can be reduced smoothly and steplessly.

Upon selecting the generator mode of the dynamotor

3

, by a computer incorporated in the power control unit

25

or arranged externally, the power control unit

25

switches the related electrical circuit. Thus, the direction of flow of the power that has thus far been supplied to the dynamotor

3

from the battery

24

is reversed, and the power is supplied toward the battery

24

from the dynamotor

3

and stored in the battery

24

. For this to be achieved, the DC voltage after rectification of the three-phase AC current generated by the dynamotor

3

as a generator is of course required to be set to a level higher than the terminal voltage of the battery

24

.

As soon as the dynamotor

3

begins to operate as a generator for charging the battery

24

under the control of the power control unit

25

, the motive power supplied from the internal combustion engine

22

through the belt

20

and the pulley

19

to the rotary shaft

11

is consumed by both the dynamotor

3

and the compressor

1

. If the rotational speed of the rotary shaft

11

dependent on the internal combustion engine

22

is constant, the amount of the motive power applied to the rotary shaft

11

by the internal combustion engine

22

is considered to be constant. Once the consumption of the motive power of the dynamotor

3

as a generator is increased, therefore, the amount of motive power that can be consumed by the compressor

1

is reduced correspondingly.

When the discharge capacity of the compressor increases excessively, therefore, the power-generating capacity of the dynamotor

3

as a generator is increased by the power control unit

25

. As a result, even in the case where the rotational speed of the rotary shaft

11

is constant, the amount of motive power consumed by the dynamotor

3

increases, so that both the amount of power generated and the amount of current charged to the battery

24

are increased. Conversely, the amount of motive power consumed by the compressor

1

decreases so that both the refrigerant discharge capacity of the compressor

1

and the cooling capacity of the air-conditioning system are decreased. This is because the increased power generation load of the dynamotor

3

increases the delay of rotation of the field portion

6

following the armature portion

18

, and the resulting increase in the difference between them reduces the rotational speed of the drive shaft

2

of the compressor

1

.

As described above, with the composite drive system for the compressor according to the first embodiment of the invention, the rotational speed of the compressor

1

can be controlled freely over a wide range from stationary state to high-speed rotation without using the electromagnetic clutch or the transmission. For this reason, various superior advantages are achieved. Specifically, the discharge capacity per unit time of the compressor

1

can be changed freely and smoothly in accordance with the cooling load, and even when the internal combustion engine

22

is stopped, the operation of the compressor

1

and the air-conditioning system can be continued by the power of the battery

24

. Also, in view of the fact that the battery

24

is charged when the system is in generator mode, the energy is not wastefully consumed, and the compressor

1

can be reduced in both size and weight. Further, even in the case where the compressor

1

is of a fixed displacement type having a predetermined discharge capacity per rotation and a simple structure, an effect can be achieved similar to that of the expensive variable displacement compressor having a complicated structure. Furthermore, the operation of the dynamotor

3

in an unloaded operation mode eliminates the need of the electromagnetic clutch, and the size of the whole system including the compressor

1

and the dynamotor

3

can be reduced as compared with the conventional system.

In addition to the qualitative description made above of the operation and effects of the composite drive system for the compressor according to the first embodiment of the invention as a typical example, a further explanation will be made specifically based on numerical values with reference to

FIGS. 5 and 6

. The diagram of

FIG. 5

shows the condition for the operation of the air-conditioning system only by the power of the battery

24

when the internal combustion engine

22

is stationary, and the condition for the operation of the air-conditioning system with the cooling capacity thereof controlled over a wide range when the internal combustion engine

22

is in operation. The abscissa represents the rotational speed of the pulley

19

and the rotary shaft

11

of the dynamotor

3

(i.e. the rotational speed of the armature portion

18

), which changes in proportion to the rotational speed of the output shaft

23

of the internal combustion engine

22

. The ordinate represents the rotational speed of the drive shaft

2

of the compressor

1

, which is identical to the rotational speed of the field portion

6

according to the first embodiment.

When the internal combustion engine

22

is stationary, the motor mode is selected by the power control unit

25

, and the power of the battery

24

is converted to the three-phase AC power and supplied to the dynamotor

3

. As a result, the dynamotor

3

is operated as a motor, so that the field portion

6

and the drive shaft

2

of the compressor

1

are rotated at the same rotational speed ΔN as the dynamotor

3

, say, at 1,000 rpm, as indicated by point M in FIG.

5

. The figure of 1,000 rpm of course is only illustrative, and the rotational speed ΔN may alternatively be 1,500 rpm or 2,000 rpm. The rotational speed ΔN can be changed freely by changing the frequency of the three-phase AC power supplied. In this way, the compressor

1

is rotationally driven by the dynamotor

3

in motor mode and the air-conditioning system can be operated with an arbitrary magnitude of the cooling capacity when the internal combustion engine

22

is stopped.

When the internal combustion engine

22

is started and the idling thereof causes the pulley

19

and the rotary shaft

11

to rotate at, for example, 1,000 rpm, on the other hand, the rotational speed of the drive shaft

2

is the sum of the rotational speed of the rotary shaft

11

(i.e. the rotational speed of the pulley

19

) and the “rotational speed ΔN of the dynamotor

3

”, as described above. Therefore, the drive shaft

2

of the compressor

1

rotates at 2,000 rpm as indicated by point S in FIG.

5

. Thereafter, even in the case where the rotational speed ΔN is maintained at a constant 1,000 rpm, the rotational speed of the drive shaft

2

increases with the rotational speed of the internal combustion engine

22

. An excessive increase in the rotational speed of the drive shaft

2

, however, would excessively increase the cooling capacity of the air-conditioning system and waste the motive power. In compliance with the instruction from the computer, therefore, the power control unit

25

automatically switches the dynamotor

3

to generator mode.

Once the dynamotor

3

has begun to operate as a generator, the rotational speed of the drive shaft

2

of the compressor

1

is decreased in accordance with the magnitude of the motive power consumed by the dynamotor

3

as described above. This change is indicated as the translation from point C to point D in FIG.

5

. In the diagram of

FIG. 5

, the portion above the straight line extending rightward up at 45° represents the motor area corresponding to the motor mode of the dynamotor

3

, and the portion below the same straight line indicates the generator area corresponding to the generator mode of the dynamotor

3

.

Also, when the system is in generator mode, the rotational speed of the drive shaft

2

of the compressor

1

is given as the sum of the rotational speed of the rotary shaft

11

(i.e. the rotational speed of the pulley

19

) and the rotational speed ΔN of the dynamotor

3

defined earlier. In generator mode, however, the rotational speed on the output side (field portion

6

) is lower than the rotational speed on the input side (rotary shaft

11

), and therefore the “rotational speed ΔN of the dynamotor

3

” defined as the difference between the rotational speeds on input and output sides assumes a negative value. Thus, the rotational speed of the rotary shaft

11

is reduced by ΔN and transmitted to the field portion

6

and the drive shaft

2

of the compressor

1

. At this point, the negative rotational speed of the dynamotor

3

is changed by controlling the amount of the current flowing in the coils

15

of the dynamotor

3

. Then, even though the rotational speed of the internal combustion engine

22

and hence the pulley

19

remains the same, the rotational speed of the drive shaft

2

changes steplessly, so that the discharge capacity of the compressor

1

and the cooling capacity of the air-conditioning system can be changed steplessly.

Even in the case where the rotational speed of the drive shaft

2

is reduced by controlling the amount of the three-phase AC current flowing in the coils

15

of the dynamotor

3

in generator mode and thus increasing the absolute value of the rotational speed ΔN of the dynamotor

3

assuming a negative value, however, the rotational speed of the drive shaft

2

of the compressor

1

is still increased if the rotational speed of the internal combustion engine

22

increases greatly. In the event that the rotational speed of the drive shaft

2

exceeds the upper limit of the preferred rotational speed range indicated by point A in FIG.

5

and may further increase along the dashed line, for example, the function to suppress the rotational speed by setting the operation of the dynamotor

3

in generator mode may reach the limit and may be incapable of working effectively any longer. This situation occurs, for example, in a case where the battery

24

is charged to 100% of the capacity thereof and has no margin to receive the power from the dynamotor

3

in generator mode.

This situation can be met by controlling the duty factor as shown in FIG.

6

. Specifically, at the time Tφ at point A in

FIG. 5

where the rotation speed of the pulley

19

is 3,000 rpm and the rotational speed of the drive shaft

2

of the compressor

1

is 2,000 rpm, the power control unit

25

disconnects the dynamotor

3

and the battery

24

from each other only for a short time. As a result, the current ceases to flow in the coils

15

of the dynamotor

3

. Therefore, the dynamotor

3

turns to unloaded operation mode in which the compressor

1

is not driven, and the rotational speed of the drive shaft

2

indicated by a solid horizontal line is decreased toward zero. Upon the lapse of the predetermined short time, the power control unit

25

reconnects the dynamotor

3

and the battery

24

for a short time to return the dynamotor

3

to generator mode. Thus, the rotational speed of the drive shaft

2

approaches the rotational speed of the pulley

19

at 3,000 rpm as indicated by a thin horizontal line. However, this state lasts only for a short time T

1

after which the coils

15

are deenergized again. By repeating the unloaded operation mode and the generator mode at short time intervals in this way, the on-off control operation is performed with the duty factor T

1

/T

2

. Thus, the abnormal increase in the rotational speed of the drive shaft

2

and the resulting otherwise excessive cooling capacity can be suppressed even in the case where the battery

24

is fully charged.

In this case, if the rotational speed of the drive shaft

2

of the compressor

1

reaches exactly the same level of 3,000 rpm as that of the pulley

19

, the motive power of the dynamotor

3

would cease to be transmitted. Therefore, the minimum difference of “the rotational speed ΔN of the dynamotor 3” is required between the rotational speed of the drive shaft

2

and that of the pulley

19

. The power generating ability of the dynamotor

3

can be maintained unless the value ΔN is zero, no matter however small it may be. Therefore, the value ΔN is minimized to reduce the electric energy supplied to the battery

24

while at the same time adjusting the discharge capacity of the compressor

1

by controlling the duty factor.

As described above, the present invention has the feature that the discharge capacity per unit time is increased and the discharge capacity can be controlled over a wide range by using the compressor

1

of a smaller capacity and driving the same compressor

1

with the small dynamotor

3

at a higher speed. Nevertheless, in the case where the size of the dynamotor

3

can be increased to generate a larger motive power, the compressor

1

of normal size may be used and the dynamotor

3

may be operated frequently in generator mode, thereby consuming most of the time for charging the battery

24

.

FIG. 7

shows the essential parts of a composite drive system of a compressor according to a second embodiment of the invention. The second embodiment is different substantively from the first embodiment shown in

FIG. 1

in that the pulley

19

has a smaller diameter and makes up a mechanism for transmitting a higher speed in a predetermined relation with the diameter of the pulley

21

shown in

FIG. 4

, and that the rotating field portion

6

of the dynamotor

3

doubles as a housing integrated with the pulley

19

thus constituting the input side of the dynamotor

3

while the armature portion

18

constitutes the output side of the dynamotor

3

correspondingly, so that the rotary shaft

11

of the dynamotor

3

is integrated with the drive shaft

2

of the compressor

1

. The other points are similar to the corresponding points of the first embodiment.

As in the second embodiment, even in the case where the field portion

6

is rotationally driven by the internal combustion engine

22

, the rotational speed equal to the sum of the rotational speed of the pulley

19

and the rotational speed ΔN of the dynamotor

3

can be similarly acquired from the armature portion

18

. In this case, ΔN is a value equal to the rotational speed of the armature portion

18

on the output side less the rotational speed of the filed unit

6

on the input side, and similarly assumes a positive value in motor mode and a negative value in generator mode. In the second embodiment, as compared with the first embodiment, the pulley

19

itself is driven at a higher speed, and therefore the discharge capacity per unit time is increased for the same small capacity of the compressor

1

. The other functions and effects of the second embodiment are similar to the corresponding ones of the first embodiment.

FIGS. 8 and 9

show the essential parts of the composite drive system for the compressor according to a third embodiment of the invention. In the dynamotor

3

, as in the second embodiment shown in

FIG. 7

, the field portion

6

makes up the input side and the armature portion

18

the output side. As shown in

FIG. 4

, the pulley

19

rotationally driven by the internal combustion engine

22

is formed integrally on the outer periphery of the field portion

6

doubling as the housing of the dynamotor

3

. The diameter of the pulley

19

is larger than in the second embodiment. The other parts of the configuration are similar to, and have substantially similar functions and effects as, the corresponding parts of the first embodiment shown in

FIGS. 1 and 2

.

FIG. 10

shows the essential parts of the composite drive system for the compressor according to a fourth embodiment of the invention. In this embodiment, the dynamotor

3

is of commutator type and is supplied with DC power for generating the DC power. In spite of the fact that the supplied power is direct current, this embodiment is similar to the third embodiment shown in

FIG. 8

in that the permanent magnets

10

are mounted on the inner surface of the field portion

6

doubling as a housing and the coils

15

are arranged on the armature portion

18

. Similarly, the pulley

19

is integrated with the field portion

6

making up the input side and the armature portion

18

makes up the output side.

The fourth embodiment is different from the third embodiment in that two concentric slip rings

16

, inner and outer, are mounted on the end surface of the housing

1

a

of the compressor

1

through an insulating member and two corresponding brushes

17

are mounted on the insulating member

26

on the inner surface of the rotating field portion

6

, that two other brushes

27

connected to the brushes

17

by a conductor not shown are arranged on the insulating member

26

in radially opposed relation to each other with the forward ends thereof in sliding contact with a plurality of commutators

28

mounted on the rotary shaft

11

through an insulating member, that a plurality of coils

15

are connected to the commutators

28

, and that the contents of the circuits of the power control unit

25

are different.

As described above, according to the fourth embodiment, the dynamotor

3

is of commutator type and is supplied with DC power and therefore has the above-mentioned configurational difference with the third embodiment. Nevertheless, the basic features of the third and fourth embodiments are not different from each other. The fourth embodiment, therefore, basically has similar functions and effects to those of each embodiment described above. When the dynamotor

3

operates in motor mode, the DC power of the battery

24

is of course supplied as it is to the coils

15

through the power control unit

25

and the commutator

28

. As long as the dynamotor

3

operates in generator mode, on the other hand, DC power is produced from the brushes

27

and therefore the power control unit only regulates the voltage thereof. Thus, the DC power is supplied to and stored in the battery

24

substantially as it is.

In each of the embodiments described above, the dynamotor

3

has permanent magnets

10

for purposes of simplifying and reducing the cost of the structure of the dynamotor

3

. Therefore, the permanent magnets

10

may safely be replaced with electromagnets composed of a coil and an iron core. Also, in spite of the fact that the permanent magnets

10

are mounted on the field portion

6

in each of the embodiments described above, common knowledge about the motor and the generator indicates that the permanent magnets can be radially mounted on the armature portion

18

while at the same time arranging the coils on the field portion

6

. Further, the power supplied to the dynamotor

3

from the power control unit

25

and produced from the dynamotor

3

may be the single-phase AC power instead of the three-phase AC or DC power unlike in the embodiments described above.

As is apparent from the configuration and the operation of the composite drive system for the compressor according to the embodiments of the invention described above, the power control unit

25

inserted between the dynamotor

3

and the battery

24

, though varied by the type of the power supplied to the dynamotor

3

, is basically required to have three functions including (1) the function of rotationally driving the dynamotor

3

as a motor, (2) the function of producing the power from the dynamotor

3

as a generator and supplying it to the battery

24

, and (3) the function of operating the dynamotor

3

in an unloaded operation mode. Two examples of an electrical circuit incorporated in the power control unit

25

for achieving these functions are shown in

FIGS. 11 and 12

. These electrical circuits are controlled by a computer (CPU)

29

arranged inside or outside the power control unit

25

. The CPU

29

performs the arithmetic operations based on the output signals of sensors for detecting the magnitude of the cooling capacity required of the air-conditioning system, the operating condition including the rotational speed and the stationary state of the internal combustion engine

22

or the storage capacity of the battery

24

or the built-in map data, etc., and outputs the required control signal to the electrical circuits in the power control unit

25

.

FIG. 11

shows an example of a circuit of the power control unit

25

employed in the case where the dynamotor

3

is a DC machine. A pair of power transistors

30

,

31

are connected in loop, and one of the two junction points is connected to the dynamotor

3

while the other junction point is connected to the battery

24

. The base of each the transistors

30

and

31

is supplied with a control signal as a voltage from the CPU

29

, and in accordance with the control signal, at least one of the two transistors

30

,

31

is turned on, or both are turned off, at the same time. In the case where the dynamotor

3

is operated in motor mode, the transistor

30

is turned on. As a result, the DC power of the battery

24

is supplied to the dynamotor

3

. The amount of the current is controlled by the transistor

30

in accordance with the magnitude of the voltage of the control signal, and therefore the discharge capacity of the compressor

1

can be controlled by changing the rotational speed ΔN of the dynamotor

3

steplessly.

Conversely, in the case where the dynamotor

3

is operated in generator mode, the transistor

31

is turned on by the CPU

29

. As a result, the DC power generated by the dynamotor

3

, which is now a generator, is supplied to and stored in the battery

24

. The amount of this current can also be controlled steplessly by the transistor

31

.

In the case where the compressor

1

is stopped, both the transistors

30

and

31

are turned off, resulting in the unloaded operation mode. The electrical circuit between the dynamotor

3

and the battery

24

is turned off, and no power is transmitted. Thus, the output side of the dynamotor

3

is deactivated, and the drive shaft

3

of the compressor

1

connected thereto is also stopped. It is not therefore necessary to use an electromagnetic clutch. The duty factor control operation can be performed by repeating the turning on/off between the disconnection in unloaded operation mode and the interlocked operation in generator mode or motor mode at short intervals of a short time.

FIG. 12

shows a circuit example of the power control unit

25

in the case where the dynamotor

3

is a three-phase AC machine. In this case, six power transistors

32

to

37

and six diodes

38

to

43

bridging the transistors, respectively, make up three circuits parallel to each other. These circuits are collectively connected to a battery

24

. The base of each of the transistors

32

to

37

is impressed with a voltage as an independent control signal from the CPU

29

. The three circuits include terminals

17

a,

17

b,

17

c,

respectively, which are connected to the three brushes

17

of the dynamotor

3

shown in

FIG. 1

, for example. The three brushes

17

in turn are connected to the coils

15

of the armature portion

18

through the three slip rings

16

in sliding contact therewith. The three slip rings

16

are shown as the slip rings

16

a

to

16

c

in FIG.

3

.

As is apparent from the circuit configuration shown in

FIG. 12

, in the case where the dynamotor

3

is operated in motor mode, this circuit operates as an inverter circuit for converting the DC power of the battery

24

to the three-phase AC power in response to the control signal of the CPU

29

. In the process, the amount of the current flowing in the three circuits can of course be controlled freely.

In the case where the dynamotor

3

making up the three-phase AC machine is operated in generator mode, on the other hand, the circuit shown in

FIG. 12

operates as a rectifier circuit for converting the three-phase AC power generated in the dynamotor

3

to DC power. At the same time as the rectification, the amount of the current and the voltage applied to the battery

24

are also controlled.

Further, the three circuits shown in

FIG. 12

can be turned off at the same time in compliance with an instruction from the CPU

29

. As a result, not only the power cannot be supplied to the dynamotor

3

but also the power cannot be recovered. Thus, the dynamotor

3

is set in unloaded operation mode, so that the compressor

1

is stopped while the internal combustion engine

22

is running, or the unloaded operation mode and the generator mode are switched to each other at internals of a short time, thereby making it possible to perform the duty factor control operation as shown in FIG.

6

.

FIGS. 13 and 14

show the essential parts of a composite drive system for the compressor according to a fifth embodiment of the invention. The dynamotor

3

according to the fifth embodiment is different from that of the embodiments described above in that the fifth embodiment includes a housing

50

fixedly mounted on the housing

51

of the compressor

1

, that a rotatable rotor

52

in the shape of a deep dish is directly coupled to the rotary shaft

11

, that a plurality of permanent magnets

10

are mounted on the inner peripheral surface of the rotor

52

, and that a fixed iron core

53

made of a magnetic material having a plurality of radial protrusions as shown in

FIG. 14

is mounted on the boss

51

a

formed to protrude axially from the housing

51

of the compressor

1

and the coils

15

are mounted on the protrusions, respectively.

These coils

15

are supplied, through wiring not shown, with the three-phase AC power from the inverter in the power control unit

25

shown in

FIG. 15

to thereby generate a rotary magnetic field on the iron core

53

. The inverter is supplied with the DC power from the battery

24

. The rotary magnetic field of the iron core

53

rotates the rotor

52

having the permanent magnets

10

, thereby rotationally driving the drive shaft

2

of the compressor

1

. This is the operation in motor mode of the dynamotor

3

according to the fifth embodiment. In this case, the coils

15

are fixed together with the iron core

53

, and therefore, as in each of the embodiments described above, the need is eliminated of the power feeding mechanism including the slip rings or the commutator and the brushes for supplying power to the coils

15

.

A dish-shaped hub

55

is mounted on the rotary shaft

11

of the dynamotor

3

through a one-way clutch

54

. The grease for lubricating the one-way clutch

54

is sealed hermetically in the cylindrical space

55

a

at the center of the hub

55

by a seal member

56

. The pulley

19

is rotatably supported by the bearing

57

mounted on the housing

50

of the dynamotor

3

and, as shown in

FIG. 4

, rotationally driven by the internal combustion engine

22

through the belt

20

. A damper

58

made of an elastic material such as rubber is interposed between the pulley

19

and the hub

55

. Further, a part of the hub

55

is formed with an annular thin portion making up a torque limiter

59

adapted to break for cutting off the transmission of an excessive torque which may be imposed.

The dynamotor

3

according to the fifth embodiment can operate not only in motor mode, but also as a generator in the case where the pulley

19

is constantly driven rotationally by the internal combustion engine

22

and the rotor

52

is rotationally driven through the hub

55

and the one-way clutch

54

. The three-phase AC power is produced to the power control unit

25

from the fixed coils

15

, and after being rectified as described above, charged to the battery

24

. This represents the operation of the dynamotor

3

in generator mode according to the fifth embodiment. When the system is in generator mode, only the lightweight rotor

52

having the permanent magnets

10

is rotated, and therefore a lesser load is imposed on the internal combustion engine

22

than for the normal alternator.

In each of the fifth and subsequent embodiments, the compressor

1

is a swash-plate compressor of a variable displacement type. However, this is only an example, and the compressor

1

is not limited to such type, but a variable displacement compressor of other types, or a compressor having a predetermined discharge capacity may be employed with equal effect. The structure and the operation of the swash-plate compressor of variable displacement type shown in the drawings are well known and therefore is not described herein.

The composite drive system for the compressor according to the fifth embodiment is configured as described above. In the case where the internal combustion engine

22

is stopped by the idle-stop control so that the compressor

1

is rotationally driven with the pulley

19

not in rotation, for example, the three-phase AC power is supplied to the coils

15

of the dynamotor

3

from the inverter in the power control unit

25

. As a result, a rotary magnetic field is formed in the fixed iron core

53

. Thus, the rotor

52

having the permanent magnets

10

is rotated thereby to rotationally drive the drive shaft

2

of the compressor

1

together with the rotary shaft

11

. In this motor mode, the provision of the one-way clutch

54

can maintain the stationary state of such portions as the hub

55

and the pulley

19

on the side of the internal combustion engine

22

. The rotational speed of the dynamotor

3

and hence the rotational speed and the discharge capacity of the compressor

1

can be freely changed by controlling the electric energy supplied to the dynamotor

3

using the power control unit

25

. This control operation can be smoothly carried out by controlling the amount of supplied current according to the duty factor.

This dynamotor

3

can be operated always in generator mode as long as the internal combustion engine constituting a main drive source is rotated except in motor mode. The rotor

52

of the dynamotor

3

according to the fifth embodiment only supports a plurality of the permanent magnets

10

, and therefore is lighter than the counterpart carrying the coils and the iron core. Therefore, the power loss of the rotor

52

is very small even when it is kept in rotation. In generator mode, the dynamotor

3

operates always as a generator and is constantly ready to charge the battery

24

. In the case where the compressor

1

is a refrigerant compressor of the air-conditioning system, therefore, the dynamotor

3

can operate as a generator even in the cold winter season when the compressor

1

is not operated. The amount of the current flowing to the battery

24

can of course be controlled freely by the power control unit

25

.

Should the compressor

1

including the composite drive system according to the fifth embodiment be locked, the torque limiter

59

portion of the hub

55

would be broken by the abnormally increased torque, and the belt

20

is prevented from breaking. Further, since a damper

58

is inserted between the hub

55

and the pulley

19

, the torque change generated when the compressor

1

is driven is absorbed and the vibration can be damped.

FIG. 15

shows the essential parts of the composite drive system for the compressor according to a sixth embodiment of the invention. The portions shared by the fifth embodiment are designated by the same reference numerals, respectively, and will not be explained again. The features of the sixth embodiment as compared with the fifth embodiment lie in that in the absence of the housing of the dynamotor

3

, the pulley

19

is rotatably supported by the rotating rotor

52

through the bearing

60

, and that the rotor

52

is rotatably supported by the boss

51

a

formed on the housing

51

of the compressor

1

through the bearing

61

.

According to the sixth embodiment, a plurality of the permanent magnets

10

are mounted on the outer peripheral surface of the cylindrical portion of the rotor

52

, and therefore the iron core

53

having the coils

15

is mounted directly on the side surface of the housing

51

of the compressor

1

in opposed relation to the permanent magnets

10

. The functions and effects of the sixth embodiment are substantially identical to those of the fifth embodiment.

FIG. 16

shows the essential parts of the composite drive system for the compressor according to a seventh embodiment of the invention. Comparison between the

FIGS. 16 and 13

apparently shows that the seventh embodiment is different from the fifth embodiment in that according to the seventh embodiment lacking the housing

50

of the dynamotor

3

, the pulley

19

is rotatably supported by the rotating rotary shaft

11

through the bearing

62

. The rotary shaft

11

itself is rotatably supported by the boss

51

a

of the housing

51

through the bearing

8

. The functions and effects of the seventh embodiment are substantially identical to those of the fifth embodiment.

FIG. 17

shows the essential parts of the composite drive system for the compressor according to an eighth embodiment of the invention. Comparison between

FIGS. 17 and 13

apparently shows that the eighth embodiment is different from the fifth embodiment in that according to the eighth embodiment, the iron core

53

having a plurality of the coils

15

is arranged on the inner peripheral surface of the housing

50

of the dynamotor

3

, and a plurality of the permanent magnets

10

are arranged on the inner peripheral surface of the rotor

52

in opposed relation to the iron core

53

. The other points and the functions and effects are similar to the corresponding points of the fifth embodiment.

FIG. 18

shows the essential parts of the composite drive system for the compressor according to a ninth embodiment of the invention. The features of the ninth embodiment lie in that the housing

50

of the dynamotor

3

covers the dynamotor

3

from the front portion thereof and then turning back toward the central portion of the dynamotor

3

followed by advancing back again forward, forms an end portion including a cylindrical portion

50

a

having a small diameter, and that the bearing

57

for rotatably supporting the pulley

19

is mounted on the outer surface of the cylindrical portion

50

a.

As a result, the axial length of the whole system can be shortened as compared with each of the embodiments described above.

The rotor

52

mounted on the rotary shaft

11

is shaped to allow for the arrangement of the bearing

57

of the pulley

19

and to circumvent rearward of the permanent magnets supported by the bearing

57

. Also, the pulley

19

is so shaped as to cover the housing

50

of the dynamotor

3

from the front part thereof, in view of the fact that the bearing

57

supporting the pulley

19

is arranged in the dynamotor

3

. The most of the pulley

19

is arranged rearward of the front end of the housing

50

. Therefore, the dynamotor

3

and the pulley

19

and the bearing

63

for supporting the one-way clutch

54

and the hub

55

can also be arranged rearward, thereby contributing to a shorter axial length of the whole system.

According to the ninth embodiment, the one-way clutch

54

is arranged at the front end of the rotor

52

, and the shield-type bearing

63

(including a shield member sealed with grease) is arranged behind the one-way clutch

54

thereby preventing the grease from leaking out of the one-way clutch

54

. In the ninth embodiment, the coils

15

and the iron core

53

are mounted on the housing

50

of the dynamotor

3

, and therefore the connector

64

for supplying power to the dynamotor

3

can be integrated with the housing

50

, thereby simplifying the configuration.

FIG. 19

shows the essential parts of the composite drive system for the compressor according to a tenth embodiment of the invention. The feature of the tenth embodiment lies in that, unlike in the ninth embodiment according to which the one-way clutch

54

directly engages a part of the rotor

52

, a collar

69

is provided as a member independent of the rotor

52

. The collar

69

is fixed by, say, pressure fitting at the forward end of the cylindrical portion

52

a

at the central of the rotor

52

. The collar

69

, which is small and independent of the rotor

52

, can be independently made of a high-class hard material or can be heat treated, and therefore the whole rotor

52

need not be fabricated of a high-class material. Also, there is no need of performing the complicated process such as the local heat treatment of only the portion of the rotor

52

engaging the one-way clutch

54

.

FIG. 20

shows the essential parts of the composite drive system for the compressor according to an 11th embodiment of the invention. In this embodiment, the bearing

57

for the pulley

19

is supported differently from the ninth and tenth embodiments. In the ninth and tenth embodiments, the bearing

57

of the pulley

19

is supported on the outer surface of the end portion including the small-diameter cylindrical portion

50

a

formed to extend toward the central portion. In the 11th embodiment, on the other hand, the bearing

57

is supported on the inner surface of the large-diameter cylindrical portion

50

b

formed at the end portion of the housing

50

covering the dynamotor

3

.

The configuration of the 11th embodiment can simplify the bearing structure of the pulley

19

and avoid the complicated shape of the housing

50

of the dynamotor

3

. In the 11th embodiment shown in

FIG. 20

, for fixing the housing

50

of the dynamotor

3

firmly on the housing

51

of the compressor

1

, a fitting portion

65

and bolts

66

are used. Also, in order to prevent the one-way clutch

54

from inclination, the one-way clutch

54

is supported on the two sides thereof by the bearings

63

,

67

. Further, for stopping the hub

55

, the cover

68

of an independent structure is mounted at the forward end of the cylindrical portion

52

a

formed axially about the center of the rotor

52

. Thus, the hub

55

is positioned axially on both sides of the bearings

63

and

67

between the cover

68

and the step

52

b

formed on the cylindrical portion

52

a.

As described above, the ninth to 11th embodiments each have a feature, in the detailed structure, useful for actually designing the dynamotor

3

integrated with the compressor

1

driven by the internal combustion engine through the belt and the pulley

19

in the air-conditioning system or the like mounted on an automobile. Nevertheless, the basic functions and effects of these embodiments are substantially identical to those of the fifth embodiment.

Number	Date	Country
2001-038589	Feb 2001	JP
2001-174660	Jun 2001	JP
2001-202655	Jul 2001	JP

Number	Name	Date	Kind
3703642	Balaguer	Nov 1972	A
3985468	Lewis	Oct 1976	A
4769993	Kawamura	Sep 1988	A
5132604	Shimane et al.	Jul 1992	A
5675203	Schulze et al.	Oct 1997	A
6234769	Sakai et al.	May 2001	B1

Number	Date	Country
U-6-87678	Dec 1994	JP
A-2000-229516	Aug 2000	JP

Composite drive system for compressor

Information

Patent Number

Date Filed

Date Issued

Inventors

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Examiners

Agents

CPC

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US

International Classifications

Term Extension

Abstract

Description

Claims

Priority Claims (3)

US Referenced Citations (6)

Foreign Referenced Citations (2)