JP2003293949A - Suction booster for compressor and controller for compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a suction booster for a compressor that reconciles a reduced size and a stabilized suction boosting effect. <P>SOLUTION: The suction booster comprises a supercharger 51 for boosting refrigerant gas sucked into compression chambers 26 of a compressor C, and an engine E for driving the supercharger 51. As the supercharger 51, a pressure wave supercharger is used. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for a refrigeration cycle, and more particularly to a suction promoting device for positively supplying a refrigerant gas to a compression chamber of the compressor, and a compressor equipped with the suction promoting device. Control device.

[0002]

2. Description of the Related Art As this type of technology, for example, there is one disclosed in Japanese Patent Laid-Open No. 172050/1993.
In the technique of this publication, a refrigerant gas is positively supplied to the compression chamber by disposing a supercharger in the refrigerant gas passage from the suction pressure region to the compression chamber.

As the supercharger, a so-called turbo type is used, which is provided with supercharging blades that turn by receiving power from the drive shaft of the compressor. The turbo type supercharger is designed to send the refrigerant gas toward the compression chamber by applying centrifugal force to the turbocharger. As described above, by providing the supercharger, the suction mass of the refrigerant gas into the compression chamber is increased, and the volumetric efficiency of the compressor can be improved.

[0004]

However, in the turbo type supercharger, if the rotational speed of the drive shaft, that is, the peripheral speed of the supercharging vanes is low, sufficient centrifugal force cannot be applied to the refrigerant gas. . Therefore, there is a problem that not only the effect of accelerating the suction of the refrigerant gas cannot be obtained, but also the supercharging vanes serve as a passage resistance to hinder the suction of the refrigerant gas into the compression chamber.

To solve this problem, the supercharging vanes may be made larger in the radial direction to increase the peripheral speed.
However, an increase in the size of the supercharging vanes leads to an increase in size of the compressor, which makes the compressor unsuitable especially for vehicle installations where the installation space is limited.

An object of the present invention is to reduce the size of the compressor and to achieve a stable suction promotion effect, and a suction promotion apparatus for a compressor, and a control apparatus for a compressor including the suction promotion apparatus. To provide.

[0007]

In order to achieve the above object, the suction promoting device according to the invention of claim 1 is provided with a supercharger for boosting the pressure of the refrigerant gas sucked into the compression chamber. Therefore, the suction mass flow rate or circulation amount of the refrigerant gas to the compression chamber is increased, and the volumetric efficiency of the compressor can be improved.

In the present invention, a pressure wave type supercharger is used as the supercharger. The pressure wave type supercharger can exhibit a sufficient supercharging effect even if the rotation speed of the supercharger drive source is low, for example. Therefore, as compared with the case of using the turbo type supercharger, it is possible to stably achieve the suction promotion effect of the compressor even if the supercharger is downsized. Further, the pressure wave type supercharger has a simple structure, and it is possible to provide the suction promoting device at low cost. For example, a mode in which the supercharger is built in the compressor can be easily embodied. Become.

According to a second aspect of the present invention, in the first aspect, the supercharger includes a low-pressure refrigerant gas introducing section, a supercharging refrigerant introducing section,
A cell and a low pressure refrigerant gas outlet are provided. The low-pressure refrigerant gas introduced into the cell via the low-pressure refrigerant gas introducing section is compressed by the supercharging refrigerant (high-pressure gas) introduced into the cell via the supercharging refrigerant introducing section. The compressed low pressure refrigerant gas is discharged from the cell to the compression chamber of the compressor via the low pressure refrigerant gas discharge portion. With this configuration, it is possible to efficiently supercharge the suction refrigerant gas by using the discharged refrigerant gas (high pressure refrigerant gas) or the liquid refrigerant (high pressure gas due to its vaporization) in the refrigeration cycle.

The "refrigeration cycle discharge pressure region" means a region between the discharge chamber of the compressor and the condenser of the external refrigerant circuit, which includes both of them. In addition, the “liquid refrigerant region of the refrigeration cycle” refers to a region between the condenser of the external refrigerant circuit and the pressure reducing device that includes both of them.

According to a third aspect of the present invention, in the second aspect, the supercharger has a supercharging refrigerant lead-out portion. The supercharging refrigerant (gas) after compressing the low-pressure refrigerant gas is led out from the cell to the suction pressure region of the refrigeration cycle via the supercharging refrigerant lead-out portion. With this configuration, the supercharging refrigerant gas expanded by the compression of the low-pressure refrigerant gas can be smoothly discharged from the cell.

In order to achieve the above object, the suction promoting device of the invention of claim 4 comprises a supercharger for boosting the pressure of the refrigerant gas sucked into the compression chamber. Therefore, the suction mass flow rate or circulation amount of the refrigerant gas to the compression chamber is increased, and the volumetric efficiency of the compressor can be improved.

In the present invention, a positive displacement type is used as the supercharger. The positive displacement supercharger can exhibit a sufficient supercharging effect even if the rotation speed of the supercharger drive source is low, for example. Therefore, as compared with the case where the turbo type supercharger is used, the suction promotion effect can be stably achieved even if the size is reduced.

According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the supercharger is mounted in a housing that houses a compression mechanism. Therefore, the number of parts of the supercharger can be reduced by sharing the housing with the compressor.

According to a sixth aspect of the present invention, in any one of the first to fourth aspects, the supercharger is arranged independently of a housing that houses a compression mechanism. Therefore, it is possible to prevent the compressor from becoming large due to the mounting of the supercharger, and it is possible to dispose the supercharger at an arbitrary position. Such an aspect is particularly suitable for mounting on a vehicle in which the arrangement space and layout of the refrigeration cycle are greatly limited.

According to a seventh aspect of the present invention, in any one of the first to sixth aspects, the compressor drive source also serves as a supercharger drive source. Therefore, it does not require a dedicated drive source for the supercharger,
The structure of the inhalation promoting device can be simplified.

According to an eighth aspect of the present invention, in any one of the first to sixth aspects, the supercharger drive source is provided separately from the compressor drive source. Therefore, the supercharging pressure of the supercharger can be stabilized without being affected by the operating state of the compressor drive source.

According to a ninth aspect of the present invention, in the suction valve mechanism of the first aspect, the suction valve mechanism of the compression mechanism is rotated in synchronization with the drive shaft to open / close a gas passage between the compression chamber and the suction pressure region. Possible rotary valves are used. Therefore, for example, it is possible to prevent the occurrence of abnormal noise or vibration due to the self-excited vibration of the reed valve, which occurs when a reed valve type intake valve mechanism is used. Further, the rotary valve can open and close the gas passage at a constant timing without being affected by fluctuations in the supercharging pressure of the supercharger. Therefore, the compressor can stably exert the compression action of the refrigerant gas.

According to a tenth aspect of the present invention, in the ninth aspect, the rotary member of the supercharger, the drive shaft, and the rotary valve are arranged on the same axis and integrated. Therefore, a complicated power transmission mechanism such as a gear mechanism or a pulley / belt mechanism is not required between the drive shaft and the rotary valve or between the drive shaft and the rotating member of the supercharger, and the supercharger is included. The configuration of the compressor can be simplified and downsized.

The invention of claim 11 is based on claim 10,
The supercharger is a pressure wave type in which the discharge pressure region of the refrigeration cycle is used as a high pressure source, and the rotating member is a rotor having a plurality of cells around its rotation axis. The pressure wave type supercharger has a simpler structure than the positive displacement type supercharger. Therefore, as described above, it is possible to easily embody the mounting of the supercharger in the housing of the compressor, and further to integrate the rotor of the supercharger with the drive shaft of the compressor and the rotary valve.

The invention of claim 12 is the same as in claim 10,
The supercharger is a pressure wave type in which a liquid refrigerant region of a refrigeration cycle is used as a high pressure source, and the rotating member is composed of a rotor having a plurality of cells around its rotation axis. The pressure wave type supercharger has a simpler structure than the positive displacement type supercharger. Therefore, as described above, it is possible to easily embody the mounting of the supercharger in the housing of the compressor, and further to integrate the rotor of the supercharger with the drive shaft of the compressor and the rotary valve.

In particular, by utilizing the liquid refrigerant region of the refrigeration cycle as the high pressure source of the supercharger, it is expected that the temperature of the housing of the compressor will be reduced by the endothermic action of the vaporization of the liquid refrigerant. Therefore, it is possible to reduce the temperature of the discharge refrigerant gas discharged from the compressor and prevent overheating of the suction refrigerant gas, and it is possible to improve the efficiency of the refrigeration cycle.

According to a thirteenth aspect of the present invention, in the eleventh or twelfth aspect, the rotor of the rotary valve and the rotor of the supercharger includes an outer peripheral surface thereof and an inner peripheral surface of a housing of the compressor slid on the outer peripheral surface. It constitutes the plain bearing surface. That is, the drive shaft is rotatably supported by the housing via the rotary valve and the rotor without using an expensive rolling bearing. In this way, the rotor of the supercharger could function also as the slide bearing of the drive shaft because the rotor has a cylindrical shape and the annular region of the outer peripheral surface of the rotor is slid on the compressor housing. It is nothing but because it adopted a pressure wave type supercharger.

The control device of the invention of claim 14 is the control device of claim 1.
13 to 13, and a supercharging pressure changing means capable of changing the supercharging pressure of the supercharger. The supercharging pressure changing means increases the supercharging pressure of the supercharger, for example, when the heat load of the refrigeration cycle is high. Therefore,
The volumetric efficiency of the compressor is enhanced, the amount of refrigerant mass circulation in the refrigeration cycle is increased, and a high heat load can be suitably accommodated. On the contrary, the supercharging pressure changing means reduces the supercharging pressure of the supercharger when the heat load of the refrigeration cycle is low. Therefore, the volumetric efficiency of the compressor is reduced, the amount of refrigerant mass circulation in the refrigeration cycle is reduced, and a low heat load can be suitably accommodated.

The invention of claim 15 is based on claim 14,
The supercharger drive source is provided separately from the compressor drive source, and the supercharging pressure changing means adjusts the supercharger drive source and the output of the supercharger drive source. And a supercharging pressure control means for controlling the supercharging pressure of the supercharger. That is, for example, when the heat load of the refrigeration cycle is high, the supercharging pressure control means increases the supercharging pressure of the supercharger by increasing the output of the drive source for the supercharger, and conversely, When the heat load is low, the output of the supercharger drive source is reduced to reduce the supercharging pressure of the supercharger.

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION First to third embodiments in which the present invention is embodied in a vehicle air conditioner will be described below.

First Embodiment (Refrigeration Cycle) As shown in FIG. 1, a refrigerant circulation circuit (refrigeration cycle) of a vehicle air conditioner has a single-head piston variable displacement compressor (hereinafter simply referred to as a compressor) C. And an external refrigerant circuit 61. The external refrigerant circuit 61 includes a condenser 62, an expansion valve 63 as a pressure reducing device, and an evaporator 6.
It is equipped with 4.

In the downstream region of the external refrigerant circuit 61, there is provided a refrigerant flow pipe 65 connecting the outlet of the evaporator 64 and the suction port 19 of the compressor C. In the upstream region of the external refrigerant circuit 61, a refrigerant flow pipe 66 that connects the discharge port 20 of the compressor C and the inlet of the condenser 62 is provided. Compressor C
Compresses the refrigerant gas introduced from the distribution pipe 65 of the external refrigerant circuit 61 through the suction port 19 and sends the compressed refrigerant gas to the distribution pipe 66 of the external refrigerant circuit 61 through the discharge port 20.

(Compressor) As shown in FIG. 1, the compressor C includes a cylinder block 11, a front housing 12 joined and fixed to a front end of the cylinder block 11, and a cylinder block 11.
The rear housing 14 is joined and fixed to the rear end of the valve / port forming body 13. Rear housing 1
A sub-housing 17 is joined and fixed to the central portion of the rear end surface of the No. 4. The cylinder block 11, the front housing 12, the rear housing 14, and the sub-housing 17 form a housing of the compressor C. The left side of the drawing is the front and the right side is the rear.

A crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing 12. The drive shaft 16 is arranged so as to pass through the crank chamber 15, and is rotatably supported by the housing of the compressor C. The rear end of the drive shaft 16 penetrates the cylinder block 11 and the rear housing 14 and reaches the sub housing 17. The drive shaft 16 is operatively connected to an engine (internal combustion engine) E that is a travel drive source of the vehicle, and is rotated by receiving power supply from the engine E.
That is, the engine E serves as a drive source for the compressor.

A lug plate 21 is integrally rotatably fixed to the drive shaft 16 in the crank chamber 15. A swash plate 23 is housed in the crank chamber 15.
The swash plate 23 is slidably supported by the drive shaft 16 and tiltably supported. The hinge mechanism 24 is interposed between the lug plate 21 and the swash plate 23. Therefore, the swash plate 23 can rotate in synchronization with the lug plate 21 and the drive shaft 16 by the hinge connection with the lug plate 21 via the hinge mechanism 24 and the support of the drive shaft 16, and at the same time, the drive shaft 16 can be rotated. It is tiltable with respect to the drive shaft 16 while being slid in the direction of the axis L.

A plurality of cylinder bores 11a (only one place is shown in the drawing) are penetratingly formed in the cylinder block 11 so as to surround the vicinity of the middle of the drive shaft 16. The single-headed piston 25 is reciprocally housed in each cylinder bore 11a. The front and rear openings of the cylinder bore 11a are closed by the valve / port forming body 13 and the piston 25.
A compression chamber 26 whose volume changes according to the reciprocating movement of the piston 25 is defined in a.

The pistons 25 are moored to the outer peripheral portion of the swash plate 23 via shoes 27. Therefore, the rotation of the swash plate 23 accompanying the rotation of the drive shaft 16 is converted into the reciprocating motion of the piston 25 via the shoe 27.

In the rear housing 14, a suction chamber 28 which constitutes the suction pressure region of the refrigerant circulation circuit and a discharge chamber 29 which constitutes the discharge pressure region are respectively formed. The suction chamber 28 is formed from the central portion of the rear housing 14 to the sub housing 17. Inhalation chamber 28
Is connected to the flow pipe 65 of the external refrigerant circuit 61 via the suction port 19 formed in the sub-housing 17. The discharge chamber 29 is formed in the rear housing 14 so as to surround the outer periphery of the suction chamber 28. Discharge chamber 29
Is connected to the flow pipe 66 of the external refrigerant circuit 61 via the discharge port 20 formed in the rear housing 14.

The refrigerant gas in the suction chamber 28 moves from the top dead center position of each piston 25 to the bottom dead center side thereof, so that the suction valve mechanism 40 arranged from the cylinder block 11 to the sub housing 17 is moved. It is sucked into the compression chamber 26 via the. The refrigerant gas sucked into the compression chamber 26 is transferred to the piston 2
5 is compressed to a predetermined pressure by moving from the bottom dead center position to the top dead center side, and is discharged into the discharge chamber 29 via the discharge port 32 and the discharge valve 33 formed in the valve / port forming body 13. . The drive shaft 16, the swash plate 23, the piston 25, and the like constitute a compression mechanism of the compressor C.

(Capacity Control Structure of Compressor) As shown in FIG. 1, in the housing of the compressor C, a bleed passage 35, an air supply passage 36 and a control valve 37 are provided. The extraction passage 35 connects the crank chamber 15 and the suction chamber 28. The bleed passage 35 includes an in-shaft passage 35a formed at the axial center of the drive shaft 16, and the inlet 3 of the in-shaft passage 35a.
5b is opened in the crank chamber 15 near the lug plate 21. The air supply passage 36 has a discharge chamber 29 and a crank chamber 15.
Communicate with.

A control valve 37, which is an electromagnetic valve, is arranged in the air supply passage 36. The opening degree of the control valve 37 is adjusted by a command from the air conditioner ECU 72, which is a control computer, based on various information provided from the external information detection means 71. The external information detection means 71 includes, for example, an air conditioner switch 73 for turning on / off the air conditioner, a temperature sensor 74 for detecting the temperature of the passenger compartment, and a temperature setter 75 for setting the temperature of the passenger compartment. Etc. are provided.

By adjusting the opening of the control valve 37, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 36 and the crank chamber 15 through the extraction passage 35.
The balance with the amount of gas discharged from is controlled, and the internal pressure of the crank chamber 15 is determined. According to the change of the internal pressure of the crank chamber 15, the difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 26 via the piston 25 is changed, and the inclination angle of the swash plate 23 is changed. As a result, the stroke of the piston 25 is changed. That is, the discharge capacity of the compressor C is adjusted.

For example, when the temperature detected by the temperature sensor 74 exceeds the temperature set by the temperature setting device 75 while the air conditioner switch 73 is turned on, the internal pressure of the crank chamber 15 decreases, that is, the valve opening degree decreases. The control valve 37 is commanded. When the internal pressure of the crank chamber 15 is reduced, the inclination angle of the swash plate 23 is increased, the stroke of the piston 25 is increased, and the discharge capacity of the compressor C is increased. If the discharge capacity of the compressor C increases, the refrigerant volume circulation amount in the refrigerant circulation circuit increases, the cooling capacity of the air conditioner increases, and the temperature of the vehicle compartment tends to decrease.

On the contrary, when the temperature detected by the temperature sensor 74 becomes lower than the temperature set by the temperature setter 75, the control valve 37 is instructed to increase the internal pressure of the crank chamber 15, that is, increase the valve opening. When the internal pressure of the crank chamber 15 increases, the inclination angle of the swash plate 23 decreases, the stroke of the piston 25 decreases, and the discharge capacity of the compressor C decreases. If the discharge capacity of the compressor C decreases, the refrigerant volume circulation amount in the refrigerant circulation circuit decreases, the cooling capacity of the air conditioner decreases, and the temperature in the vehicle compartment tends to rise.

(Suction Valve Mechanism of Compressor) As shown in FIG. 1, in the cylinder block 11, the cylinder bore 1
A valve accommodating chamber 42 is formed in the center surrounded by 1a. The valve accommodating chamber 42 has a circular cross section. The valve accommodating chamber 42 and each compression chamber 26 are communicated with each other via a suction communication passage 43 formed in the cylinder block 11.

A rotary valve 41 is rotatably housed in the valve housing chamber 42. The rotary valve 41 has a cylindrical shape. The rotary valve 41 is integrally formed at an intermediate portion of the drive shaft 16 that passes through the valve housing chamber 42. Therefore, the rotary valve 41 is rotated in synchronization with the rotation of the drive shaft 16, that is, the reciprocating movement of the piston 25. It should be noted that the rotary valve 41 is integrally formed on the drive shaft 16 so that the structure of the intake valve mechanism 40 is simplified as compared with the case where the rotary valve 41 is formed as a separate body (this aspect does not depart from the gist of the invention). Can be planned.

At the axial center position of the drive shaft 16, from the intermediate portion where the rotary valve 41 is formed to the sub housing 17
An introduction passage 44 having a diameter larger than that of the in-shaft passage 35a is formed toward the rear end portion located inside. The introduction passage 44 communicates with the suction chamber 28 on the rear side, and the outlet 35c of the above-mentioned in-shaft passage 35a is opened on the front side. Therefore, the introduction passage 44 constitutes a part of the extraction passage 35.

The outer peripheral surface 41a of the rotary valve 41 is formed with a suction guide groove 45 which is in constant communication with the introduction passage 44 in a constant circumferential section. This suction guide groove 45
The suction communication passage 43 and the introduction passage 44 form the suction chamber 28.
And a refrigerant gas passage between the compression chamber 26 and the compression chamber 26. The rotary valve 41 opens and closes this refrigerant gas passage by its rotation.

That is, the rotary valve 41 is constructed so that when the piston 25 moves to the suction stroke, the suction guide groove 4
5 is passed in the direction of opening the suction communication passage 43 of the cylinder block 11. Therefore, the refrigerant gas in the suction chamber 28 is
Introduction passage 44 and suction guide groove 45 of the rotary valve 41
In addition, it is sucked into the compression chamber 26 via the suction communication passage 43 of the cylinder block 11.

At the end of the suction stroke of the piston 25, the rotary valve 41 passes in the direction in which the suction guide groove 45 closes the suction communication passage 43, and the suction of the refrigerant gas into the compression chamber 26 is stopped. When the piston 25 is moved to the discharge stroke, the outer peripheral surface 41a of the rotary valve 41 holds the suction communication passage 43 in a closed state, and the compression of the refrigerant gas and the discharge to the discharge chamber 29 are not hindered.

(Suction Promoting Device) As shown in FIG. 2, the compressor C is provided with a suction promoting device for positively supplying the refrigerant gas to the compression chamber 26 thereof. The supercharger 51 constituting the suction promoting device is a pressure wave type supercharger (so-called pressure wave supercharger), and is attached to the housing of the compressor C.

That is, the suction chamber 28 is arranged coaxially with the valve accommodating chamber 42 on the rear side of the valve accommodating chamber 42. The suction chamber 28 has a circular cross section with a diameter larger than that of the valve accommodating chamber 42. Rear housing 14
And the inner wall surface 2 of the suction chamber 28 in the sub housing 17.
8a is formed. A front wall surface 28 b that closes the front opening of the suction chamber 28 is formed in the cylinder block 11 and the rear housing 14. A rear wall surface 28c that closes the rear opening of the suction chamber 28 is formed in the sub housing 17.

As shown in FIGS. 2 and 3, the compressor C is
In the housing, the cylindrical rotor 52 as a rotating member that constitutes the supercharger 51 is rotatably accommodated in the suction chamber 28. An attachment hole 52a is formed through the center of the rotor 52. On the outer peripheral side of the mounting hole 52a in the rotor 52, a plurality (12 in the present embodiment) of cells 53 are formed around the rotation center axis line. Each cell 53 is opened on the front side and the rear side of the rotor 52 (front opening 53a and rear opening 53b).

The rear end portion of the drive shaft 16 extends rearward beyond the valve accommodating chamber 42 and reaches the rear wall surface 28c in the suction chamber 28. The rotor 52 is externally fitted and fixed to the rear end portion of the drive shaft 16 through a mounting hole 52a. That is, the rotor 52, the drive shaft 16, and the rotary valve 41 are arranged on the same axis L and integrated. Therefore, the rotor 52 is synchronized with the rotation of the drive shaft 16 and the inner peripheral wall surface 28 a and the front and rear wall surfaces 2 of the suction chamber 28.
It is rotated about the axis L while sliding on 8b and 28c. That is, in the suction promoting device, the supercharger drive source for driving the supercharger 51, in other words, rotationally driving the rotor 52, is provided by the engine E that also serves as the compressor drive source.

The rear end side of the drive shaft 16 does not use a rolling bearing, and the outer peripheral surface 4 of the rotary valve 41 is
It is rotatably supported by the housing of the compressor C via the outer peripheral surface 52b of the rotor 1a and the rotor 1a. That is, the rotary valve 41 and the rotor 52 are
a, 52b and the inner peripheral surface 42a of the valve housing chamber 42 and the inner peripheral wall surface 28a of the suction chamber 28, which slide on the outer peripheral surfaces 41a, 52b, receive the radial load acting on the rear end side of the drive shaft 16. It constitutes a plain bearing surface for acceptance.

As shown in FIGS. 2 and 4, the suction chamber 2
On the front wall surface 28b of No. 8, almost 1 of the cell 53 of the rotor 52 is
A supercharging refrigerant introduction groove 55 as a supercharging refrigerant introducing portion is formed in a region facing each other. Rear housing 1
4 and the valve / port forming body 13 at the joint portion, the supercharging refrigerant introduction groove 55 and the discharge chamber 2 as the high pressure source of the supercharger 51.
A communication hole 56 that always communicates with 9 is formed. Therefore, a part of the high-pressure discharged refrigerant gas flowing from the discharge chamber 29 to the discharge port 20 is introduced into the supercharge refrigerant introduction groove 55 as the supercharge refrigerant. A flow rate adjusting nozzle (not shown) is interposed between the discharge chamber 29 and the supercharging refrigerant introduction groove 55.

As shown in FIG. 4, on the front wall surface 28b of the suction chamber 28, from the position where approximately one cell 53 is separated from the supercharging refrigerant introduction groove 55 in the rotation direction of the rotor 52, A supercharging refrigerant lead-out groove 57 as a supercharging refrigerant lead-out portion is formed in a region facing approximately two of 53. As shown in FIG. 6, the supercharging refrigerant lead-out groove 57 is
A discharge passage 58 formed in the rear housing 14 communicates with an ejector 69 arranged in a flow pipe 65. The ejector 69 is L-shaped and is opened toward the downstream side (the suction port 19 side) of the flow pipe 65.

As shown in FIGS. 2 and 5, the suction chamber 2
The rear wall surface 28c of the rotor 8 has approximately five cells 53 of the rotor 52.
Intake gas introduction grooves 59 as low-pressure refrigerant gas introduction portions are formed in the regions facing each other. Intake gas introduction groove 5
9 is always connected to the suction port 19. In the rear wall surface 28c of the suction chamber 28, from a position where approximately one cell 53 is separated from the suction gas introduction groove 59 in the rotation direction of the rotor 52, a region facing approximately four cells 53, and a drive. A suction gas lead-out groove 60 as a low-pressure refrigerant gas lead-out portion is provided in a region of the shaft 16 facing the rear opening 44a of the introduction passage 44.
Are formed. That is, the suction gas lead-out groove 60 and the introduction passage 44 are always in communication with each other.

FIG. 6 is a schematic diagram in which the rotational movement of the rotor 52 is linearly developed and the swiveling of the cell 53 around the axis L is replaced by downward movement. As shown in this figure, the front opening 53a of each cell 53 is communicated with the supercharging refrigerant introduction groove 55 by the rotation of the rotor 52, is closed by the front wall surface 28b of the suction chamber 28, and is supercharging refrigerant outlet groove 57.
The communication with and the closing by the front wall surface 28b of the suction chamber 28 are repeated in the same order.

The rear opening 53b of each cell 53 communicates with the intake gas lead-out groove 60 by the rotation of the rotor 52,
The closing by the rear wall surface 28c of the suction chamber 28, the communication with the suction gas introduction groove 59, and the closing by the rear wall surface 28c of the suction chamber 28 are repeated in the same order. In each cell 53, the start of communication of the rear opening 53b with the intake gas lead-out groove 60 is performed earlier than the start of communication of the front opening 53a with the supercharging refrigerant introduction groove 55.

Then, by the rotation of the rotor 52,
When the front opening 53a of the cell 53 filled with the low-pressure suction refrigerant gas from the suction port 19 communicates with the supercharging refrigerant introduction groove 55, the high-pressure discharge refrigerant gas enters into the cell 53.
Therefore, a pressure wave (compression wave) is generated in the cell 53 due to the contact between the suction refrigerant gas and the discharge refrigerant gas, and the suction refrigerant gas is compressed. At this point, the rear opening 53b of the cell 53 has already been communicated with the intake gas lead-out groove 60, so that the intake refrigerant gas compressed and pressurized in the cell 53 is
The gas is discharged into the suction gas lead-out groove 60 and further sent to the compression chamber 26 via the suction valve mechanism 40. Therefore, the suction mass of the refrigerant gas into the compression chamber 26 is increased, and the volumetric efficiency of the compressor C is improved.

In the cell 53 from which the compressed suction refrigerant gas has been discharged, the front opening 53a communicates with the supercharging refrigerant discharge groove 57, whereby the expanded discharge refrigerant gas is discharged and the rear portion By communicating the opening 53b with the suction gas introduction groove 59, the low-pressure suction refrigerant gas from the suction port 19 is refilled. The expanded discharge refrigerant gas discharged from the cell 53 is moved into the flow pipe 65 through the discharge passage 58 and the ejector 69, merges with the suction refrigerant gas moved from the evaporator 64, and is led to the suction port 19. Sent.

The present embodiment having the above-mentioned configuration has the following effects. (1) As the supercharger 51, a pressure wave type is used. The pressure wave type supercharger 51 can exhibit a sufficient supercharging effect even if the rotation speed of the engine E is low, for example. Therefore,
Compared with the case of using a turbo type supercharger, the supercharger 51
Even if the size of the compressor C is reduced, the suction promotion effect of the compressor C (improvement of the volumetric efficiency of the compressor C) can be stably achieved.

(2) As the high pressure source of the pressure wave type supercharger 51, the discharge pressure region in the refrigerant circulation circuit is used. Therefore, compared with the case where a high-pressure source is set in a place other than the refrigerant circulation circuit, it is possible to efficiently supercharge the sucked refrigerant gas.

(3) The supercharger 51 discharges the discharged refrigerant gas after compressing the sucked refrigerant gas from the cell 53 to a suction pressure region which is a low pressure region of the refrigerant circulation circuit (in the present embodiment, the suction pressure region is higher than that of the supercharger 51). Discharge to the upstream side). Therefore, the expanded discharged refrigerant gas can be smoothly drawn out from the cell 53, and the supercharging performance of the supercharger 51 is improved.

(4) The supercharger 51 is mounted on the housing of the compressor C. Therefore, by sharing the housing with the compressor C, the number of parts of the supercharger 51 can be reduced. Further, for example, when the air conditioner is mounted on the vehicle, the compressor C and the supercharger 51 can be handled together, which improves workability.

(5) The engine E that drives the compressor C
It also serves as a drive source for the supercharger 51. Therefore, a dedicated supercharger drive source is not required, and the structure of the suction promoting device can be simplified.

(6) A rotary valve 41 is used in the intake valve mechanism 40 of the compressor C. Therefore, for example, when a reed valve type intake valve mechanism is used (this aspect does not depart from the gist of the present invention), occurrence of abnormal noise or vibration due to self-excited vibration of the reed valve is prevented. can do. Further, the rotary valve 41 opens and closes the gas passage to the compression chamber 26 at a constant timing without being affected by the fluctuation of the supercharging pressure of the supercharger 51 caused by the fluctuation of the rotation speed of the engine E, for example. be able to. Therefore, the compressor C can stably exert the compression action of the refrigerant gas.

(7) Rotor 52 of supercharger 51 and drive shaft 1
6 and the rotary valve 41 are arranged on the same axis L and integrated. Therefore, a complicated power transmission mechanism such as a gear mechanism or a pulley / belt mechanism is not required between the drive shaft 16 and the rotary valve 41 or between the drive shaft 16 and the rotor 52, and the supercharger 51 is included. The configuration of the compressor C can be simplified and downsized.

(8) By integrating the rotary valve 41 and the rotor 52 with the drive shaft 16, the rotary valve 41
The outer peripheral surface 41a of the rotor and the outer peripheral surface 52b of the rotor 52 can also serve as sliding bearing surfaces for receiving the radial load acting on the rear end side of the drive shaft 16. Therefore, it is not necessary to use an expensive rolling bearing for the rear end of the drive shaft 16, and the compressor C can be provided at a low cost. In this way, the rotor 52 could also function as the slide bearing of the drive shaft 16 because the rotor 52 has a cylindrical shape, and the annular region of the outer peripheral surface 52b of the rotor 52 slides on the housing of the compressor C. The pressure wave type supercharger 51 is adopted.

(9) The pressure wave type supercharger 51 has a simple structure as compared with, for example, a positive displacement type supercharger. Therefore, the inhalation promoting device can be provided at low cost. Further, as in the present embodiment, the supercharger 51 for the housing of the compressor C is provided.
Installation, and further, the rotor 52 of the supercharger 51 and the compressor C
The drive shaft 16 and the rotary valve 41 can be easily integrated.

Second Embodiment FIG. 7 shows a second embodiment. Below is the first
Only differences from the embodiment will be described, and the same or corresponding members as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

(Compressor) In this embodiment, the compressor C is a double-headed piston type fixed displacement type.

That is, the swash plate 23 is fixed to the drive shaft 16, and the capacity control structures 35 to 37 are removed from the housing of the compressor C. The group of cylinder bores 11a is disposed not only on the rear side but also on the front side in the housing of the compressor C, and the piston 25 is a double-head type that divides the compression chamber 26 in each of the front and rear cylinder bores 11a. ing. Therefore, on the front side of the housing of the compressor C as well as on the rear side, the suction valve mechanism 40 including the rotary valve 41 and the valve / port forming body 13 are formed.
(Discharge port 32 and discharge valve 33) are provided.

In the front and rear suction valve mechanisms 40, the introduction passage 44 is communicated with the crank chamber 15 via a communication passage 49 formed in the drive shaft 16 and the swash plate 23. The crank chamber 15 communicates with the flow pipe 65 of the external refrigerant circuit 61 via the suction port 19. The front-side and rear-side discharge chambers 29 are communicated with the flow pipe 66 of the external refrigerant circuit 61 via the discharge muffler 11b formed in the cylinder block 11 and the discharge port 20.

(Inhalation Accelerator) In the present embodiment, the suction accelerator is a supercharger 51 arranged independently of the housing of the compressor C, and a supercharger drive source for driving the supercharger 51. It is composed of an electric motor M. That is, the supercharger 51 uses the compressor C to house the rotor 52 and the like.
Dedicated electric motor M provided separately from the engine E and having a housing 81 different from the housing of
The rotor 52 is rotationally driven by. In addition, supercharger 5
1 and the electric motor M may be integrated or may be separate bodies.

The housing 81 of the supercharger 51 is provided with a supercharging refrigerant introduction groove 55, a supercharging refrigerant derivation groove 57, a suction gas introduction groove 59 and a suction gas derivation groove 60.
A supply pipe 82 branched from the distribution pipe 66 of the external refrigerant circuit 61 is connected to the supercharging refrigerant introduction groove 55. A return pipe 83, which is connected to the flow pipe 65 on the upstream side (the evaporator 64 side) of the supercharger 51, is connected to the supercharging refrigerant lead-out groove 57. The external refrigerant circuit 6 is provided in the intake gas introduction groove 59.
The upstream side (evaporator 64 side) of the first circulation pipe 65 is connected. The downstream side (intake port 19 side) of the flow pipe 65 is connected to the intake gas lead-out groove 60.

(Compressor control device) The rotation speed (output) of the electric motor M is adjusted by a command from the air conditioner ECU 72 as the boost pressure control means based on various information provided from the external information detection means 71. It The electric motor M and the air conditioner ECU 72 constitute a supercharging pressure changing means capable of changing the supercharging pressure of the supercharger 51.

That is, for example, when the temperature detected by the temperature sensor 74 exceeds the temperature set by the temperature setter 75 while the air conditioner switch 73 is on, the electric motor M is instructed to increase the rotation speed. When the rotation speed of the electric motor M increases, the supercharging pressure of the supercharger 51 increases, and the volumetric efficiency of the compressor C increases. Therefore, the refrigerant mass circulation amount in the refrigerant circulation circuit increases, the cooling capacity of the air conditioner increases, and the temperature of the vehicle interior tends to decrease.

On the contrary, when the temperature detected by the temperature sensor 74 becomes lower than the temperature set by the temperature setter 75, the electric motor M is instructed to decrease the rotation speed. When the rotation speed of the electric motor M decreases, the supercharging pressure of the supercharger 51 decreases, and the compressor C
The volume efficiency of is reduced. Therefore, the refrigerant mass circulation amount in the refrigerant circulation circuit decreases, the cooling capacity of the air conditioner decreases, and the temperature of the vehicle interior tends to increase.

In the present embodiment having the above-mentioned structure, in addition to the same effects as (1) to (3), (6) and (9) of the first embodiment, the following effects are also obtained. (1) The supercharger 51 is arranged independently of the housing of the compressor C. Therefore, it is possible to prevent the compressor C from becoming large due to the mounting of the supercharger 51, and
Can be arranged at any position. Such an aspect is particularly suitable for mounting on a vehicle in which the arrangement space and layout of the refrigerant circulation circuit are greatly limited.

(2) The supercharger 51 is driven by a dedicated electric motor M provided separately from the engine E. Therefore, the supercharging pressure of the supercharger 51 can be stabilized without being affected by the operating state of the engine E. Further, for example, by adjusting the output of the electric motor M as necessary, the supercharging pressure of the supercharger 51 can be arbitrarily externally adjusted.

(3) The air conditioner ECU 72 adjusts the cooling capacity of the air conditioner by adjusting the supercharging pressure of the supercharger 51 according to the heat load of the refrigeration cycle. Therefore, even by using the fixed-capacity compressor C, which has a simpler structure than the variable-capacity type, it is possible to perform fine air-conditioning, which simplifies the configuration of the air-conditioning device and improves the air-conditioning feeling. It becomes possible to be compatible in two dimensions.

(4) Supercharger 5 by air conditioner ECU 72
The change of the supercharging pressure of 1 is performed by adjusting the rotation speed of the electric motor M that drives the supercharger 51. Therefore,
For example, as compared with the case where the supercharging pressure control valve is arranged on the refrigerant passage between the high pressure source and the supercharger 51 (see FIG. 7), the refrigerant circulation circuit is not complicated and the weight is not increased. As a result, the supercharging pressure changing means can be embodied.

Third Embodiment FIGS. 8 to 10 show a third embodiment. Only the differences from the first embodiment will be described below, and the first
The same or corresponding members as those in the embodiment are designated by the same reference numerals and the description thereof will be omitted.

(Inhalation promoting device) In the present embodiment, the high pressure source of the supercharger 51 is set in the liquid refrigerant region of the refrigeration cycle.

That is, as shown in FIG. 8, the connection between the discharge chamber 29 of the compressor C and the supercharging refrigerant introduction groove 55 of the supercharger 51 is blocked by the elimination of the communication hole 56.
One end of a communication passage 76 formed in the rear housing 14 and the sub housing 17 is connected to the supercharging refrigerant introduction groove 55. The other end of the communication passage 76 is connected to a refrigerant passage (liquid refrigerant region) between the condenser 62 and the expansion valve 63 via an external pipe 77. A fixed throttle 78 is arranged in the middle of the external pipe 77. Therefore, the external refrigerant circuit 6
From the liquid refrigerant region of No. 1, a small amount of liquid refrigerant determined by the throttle diameter of the fixed throttle 78 is sent toward the supercharger 51.

As shown in FIGS. 9 and 10, the supercharging refrigerant lead-out groove 57 is formed in a region facing approximately 9.5 cells 53. The supercharging refrigerant outlet groove 57 communicates with the introduction passage 44 of the intake valve mechanism 40 via a communication groove 79 formed through the outer peripheral wall of the drive shaft 16.

The liquid refrigerant from the liquid refrigerant region of the external refrigerant circuit 61 is heated by the high temperature inside the housing of the compressor C on the way to the supercharging refrigerant introducing groove 55 or the supercharging refrigerant introducing groove 55. The gas is vaporized and boosted, and the compressed refrigerant gas in the cell 53 is compressed. The supercharging refrigerant gas expanded by compressing the suction refrigerant gas is discharged from the cell 53 to the introduction passage 44 of the suction valve mechanism 40 via the supercharging refrigerant outlet groove 57 and the communication groove 79, and the rear opening 44a. From the compressed suction refrigerant gas and sent to the compression chamber 26.

In the present embodiment having the above-mentioned structure, in addition to the same effects as (1), (4) to (9) of the first embodiment, the following effects are also obtained. (1) The liquid refrigerant region of the external refrigerant circuit 61 is used as the high pressure source of the pressure wave supercharger 51. Therefore, compared with the case where a high-pressure source is set in a place other than the refrigerant circulation circuit, it is possible to efficiently supercharge the sucked refrigerant gas. Also,
The temperature of the housing of the compressor C is reduced by the endothermic action due to the vaporization of the liquid refrigerant. Therefore, it is possible to reduce the temperature of the discharge refrigerant gas discharged from the compressor C and prevent overheating of the suction refrigerant gas, and it is possible to improve the efficiency of the refrigeration cycle.

(2) The supercharger 51 supplies the supercharging refrigerant gas, which is obtained by compressing the suction refrigerant gas, from the cell 53 to the suction pressure area which is a low pressure area of the refrigerant circulation circuit (in the present embodiment, the supercharger 51). To the downstream side). Therefore, the expanded supercharging refrigerant gas can be smoothly discharged from the cell 53, and the supercharging performance of the supercharger 51 is improved.

(3) The supercharger 51 introduces the supercharging refrigerant gas, which is obtained by compressing the suction refrigerant gas, from the cell 53 through the supercharging refrigerant outlet groove 57 and the communication groove 79 into the intake valve mechanism 40. Discharge to the passage 44. Therefore, for example, the configuration is simpler than that of the first embodiment in which the supercharging refrigerant gas is discharged from the supercharging refrigerant outlet groove 57 to the flow pipe 65 via the discharge passage 58 and the ejector 69. Further, the supercharging refrigerant lead-out groove 57
Since the introduction passage 44 and the introduction passage 44 are communicated with each other through the communication groove 79 at the shortest distance, the supercharging refrigerant gas can be more smoothly discharged from the cell 53, and the suction refrigerant gas is sucked into the cell 53. Be promoted.

The following embodiments can be carried out without departing from the spirit of the present invention. -A positive type is used as the supercharger 51 by changing the first to third embodiments. Examples of the positive displacement supercharger 51 include those shown in FIGS. 11 to 13.
The supercharger 51 of FIG. 11 is a screw type having a pair of screw-shaped rotors 91 as rotating members. The supercharger 51 shown in FIG. 12 has a two-leaf rotor (not shown, but may have a three-lobed shape or a three-dimensionally twisted shape) as a rotating member.
It is a roots type with two pairs. Supercharger 51 of FIG.
Is a scroll type equipped with a fixed scroll 93 and a movable scroll 94 as a rotating member.

In the positive displacement supercharger 51 described above, the rotational speed of the engine E (when the first or third embodiment is changed) or the electric motor M (when the second embodiment is changed) for driving the supercharger 51. Even if it is low, a sufficient supercharging effect can be achieved.
Therefore, the same effect as (1) of the first embodiment can be obtained. Further, for example, when the first embodiment is changed,
The same effects as (4) to (7) of the first embodiment are obtained, and when the second embodiment is changed, (6) of the first embodiment and (1) to (4 of the second embodiment. ) Also has the same effect.

In addition, since the screw type supercharger 51 shown in FIG. 11 can be used at high speed, it is more advantageous for downsizing. The roots-type supercharger shown in FIG. 12 has the advantages that the volume efficiency and the heat insulation efficiency are good, the supercharging performance is excellent, and that the high-frequency operating noise that causes annoyance is small.

The scroll type supercharger shown in FIG. 13 has an advantage of excellent quietness. Further, since it is necessary to rotate only the movable scroll 94, the compressor C can be easily attached to the housing as compared with the type in which a plurality of rotating members are rotated. Further, the suction refrigerant gas that has been compressed is discharged from the central portions of the scrolls 93 and 94. Therefore, the combination with the rotary valve 41 that introduces the suction refrigerant gas from the central portion (introduction passage 44) of the drive shaft 16 makes it easier to mount the compressor C on the housing.

Examples of positive displacement type superchargers other than those shown in FIGS. 11 to 13 include a piston type and the like. The supercharging pressure adjusting valve 87, which is a solenoid valve that constitutes supercharging pressure changing means, is provided on the supply pipe 82 as shown in FIG. Arrange. The supercharging pressure adjusting valve 87 adjusts the supply amount of the discharged refrigerant gas to the supercharger 51 according to the opening degree of the valve. That is, the supercharging pressure of the supercharger 51 can be adjusted by adjusting the valve opening degree of the supercharging pressure adjusting valve 87. And this supercharging pressure control valve 8
The opening degree of 7, that is, the distribution amount of the discharged refrigerant gas from the compressor C to the supercharger 51 is adjusted by a command of the air conditioner ECU 72 based on various information provided from the external information detection means 71.

In the first embodiment, the above-mentioned "other example" of FIG. 7 is provided on the communication hole 56 which communicates the discharge chamber 29 of the compressor C with the supercharging refrigerant introduction groove 55 of the supercharger 51. A supercharging pressure control valve 87 similar to the above should be provided. Then, the supercharging pressure adjusting valve 87 allows the supercharging pressure of the supercharger 51 to be adjusted from the outside.

Fixed aperture 78 in the third embodiment
Is changed to a variable throttle capable of changing the throttle amount in accordance with a command from the air conditioner ECU 72 (the same concept as the supercharging pressure control valve 87 shown in the “other example” of FIG. 7). The amount of liquid refrigerant supplied to the supercharger 51, that is, the supercharging pressure of the supercharger 51, can be adjusted from the outside by a variable throttle.

In the first to third embodiments, the supercharger 51 uses the supercharging refrigerant gas expanded by compressing the suction refrigerant gas from the cell 53 via the supercharging refrigerant discharge groove 57. The suction pressure region of the circulation circuit (the flow pipe 65 in the first and second embodiments, the introduction passage 44 in the third embodiment) is discharged. However, the invention is not limited to this, and the supercharging refrigerant lead-out groove 57 is removed from the supercharger 51 so that the expanded supercharging refrigerant gas is led out from the cell 53 together with the compressed intake refrigerant gas. It may be configured to discharge into the groove 60. Alternatively, the expanded supercharging refrigerant gas may be discharged from the cell 53 to the discharge pressure region of the refrigerant circulation circuit via the supercharging refrigerant lead-out groove 57.

The supercharger 51 of the first to third embodiments
Is the rear opening 53b in each cell 53 of the rotor 52.
The start of the communication with the intake gas lead-out groove 60 was earlier than the start of the communication with the supercharging refrigerant introduction groove 55 of the front opening 53a. However, the present invention is not limited to this, and in each cell 53, the start of communication of the rear opening 53b with the intake gas lead-out groove 60 is delayed from the start of communication of the front opening 53a with the supercharging refrigerant introduction groove 55. Good.

By modifying the first or third embodiment, the rotor 52 of the supercharger 51 is arranged separately from the drive shaft 16. Then, a dedicated electric motor for driving the rotor 52 should be attached to the housing of the compressor C.

Modification of the first or third embodiment to mount an electric motor for driving the compression mechanism in the housing of the compressor C. That is, embodying the present invention in the electric compressor C. In this case, the compressor C (compression mechanism) may be configured to be driven only by the electric motor, or a so-called hybrid drive type in which the drive by the engine E and the drive by the electric motor are switched according to the situation. It may be. In the former case, the electric motor serves as the drive source for the compressor and the electric motor for the compressor in the latter case.

By modifying the second embodiment, the electric motor M is deleted and the drive source of the supercharger 51 is the engine E.
To do. That is, the present invention relates to the compressor C and the supercharger 51.
Can be embodied also in a mode in which the respective drive sources are shared by the engine E while the above are separately configured.
In this embodiment, the adjustment of the supercharging pressure of the supercharger 51 is performed as shown in FIG.
The supercharging pressure control valve 87 described in the other example may be used.

By modifying the first to third embodiments, the exhaust region (exhaust gas) of the engine E is used as the high pressure source of the pressure wave type supercharger 51. The compressor to which the suction promotion device or the control device of the present invention is applicable is not limited to the piston type described in the above embodiment, and may be, for example, a scroll type or a vane type.

The technical idea that can be understood from the above embodiment will be described. (1) The compressor drive source also serves as a supercharger drive source, and the supercharger is mounted in a housing that houses a compression mechanism, and the rotating member and the compression mechanism that configure the supercharger are included. The suction promoting device for a compressor according to any one of claims 1 to 4, wherein the drive shafts are arranged on the same axis and integrated.

(2) The supercharger is a pressure wave type in which the discharge pressure region of the refrigeration cycle is used as a high pressure source, and the rotating member is a rotor having a plurality of cells around its rotation axis. A suction promoting device for a compressor according to the first idea.

(3) The supercharger is a pressure wave type having a high pressure source in a liquid refrigerant region of a refrigeration cycle, and the rotating member is a rotor having a plurality of cells around its rotation axis. A suction promoting device for a compressor according to the first idea.

(4) The rotor constitutes a slide bearing surface by the outer peripheral surface and the inner peripheral surface of the housing of the compressor slid on the outer peripheral surface, and the drive shaft is rotated by the rotor through the rotor. The suction promoting device for a compressor according to the above-mentioned technical idea (2) or (3), which is supported so as to be possible.

(5) An air conditioner comprising the suction promoting device according to any one of claims 1 to 13 or the technical ideas (1) to (4). (6) The supercharger of the suction promoting device is of a pressure wave type using a discharge pressure region or a liquid refrigerant region of the refrigeration cycle as a high-pressure source, and the supercharging pressure changing means changes from the discharge pressure region or the liquid refrigerant region. Supercharging pressure control valve that controls the amount of supercharging refrigerant supplied to the supercharger, and supercharging pressure control that controls the supercharging pressure of the supercharger by adjusting the opening of this supercharging pressure control valve. 15. The control device for the compressor according to claim 14, further comprising means.

(7) An air conditioner comprising the compressor control device according to claim 14 or claim 15 or the technical idea (6).

[0108]

According to the present invention having the above-mentioned structure, the miniaturization and
It is possible to provide a suction promoting device for a compressor that achieves stable suction promoting effect.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a single-head piston variable displacement compressor.

FIG. 2 is an enlarged view of a main part of FIG.

3 is a sectional view taken along line 1-1 of FIG.

4 is a sectional view taken along line 2-2 of FIG.

5 is a sectional view taken along line 3-3 of FIG.

FIG. 6 is a schematic diagram of a supercharger in which the rotational movement of the rotor is linearly developed.

FIG. 7 is a longitudinal sectional view of a double-headed piston type fixed displacement compressor according to a second embodiment.

FIG. 8 is an enlarged cross-sectional view of a main part of a compressor showing a third embodiment.

9 is a sectional view taken along line 4-4 of FIG.

FIG. 10 is a schematic diagram of a supercharger in which the rotational movement of the rotor is linearly developed.

FIG. 11 is a schematic view of a screw type supercharger showing another example.

FIG. 12 is a schematic view of a roots-type supercharger showing another example.

FIG. 13 is a schematic view of a scroll type supercharger showing another example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 11 ... Cylinder block which comprises the housing of a compressor, 12 ... The same front housing, 14 ... The same rear housing, 16 ... The drive shaft which comprises a compression mechanism, 17
... A sub-housing constituting a compressor housing, 23
... Swash plate that constitutes the compression mechanism, 25 ... Similarly piston, 2
6 ... Similarly, compression chamber, 28 ... Suction chamber as suction pressure region of refrigeration cycle, 28a ... Inner wall surface of suction chamber constituting slide bearing surface, 29 ... Discharge chamber as discharge pressure region of refrigeration cycle, 40 ... Suction Valve mechanism, 41 ... Rotary valve, 41a ... Outer peripheral surface of rotary valve constituting slide bearing surface, 42a ... Inner peripheral surface of valve housing chamber constituting slide bearing surface, 51 ... Supercharger, 52 ... Supercharger Rotor as rotating member, 53 ... Cell, 55 ... Supercharging refrigerant introducing groove as supercharging refrigerant introducing section, 57 ... Supercharging refrigerant outlet groove as supercharging refrigerant outlet section, 59 ... Low-pressure refrigerant gas introduction Intake gas introduction groove as a portion, 60 ... Intake gas lead-out groove as a low pressure refrigerant gas lead-out portion, 61 ... External refrigerant circuit having a liquid refrigerant region and forming a refrigeration cycle, 72 ... Salary Air conditioning EC as a control means
U, C ... Compressor which constitutes refrigeration cycle, E ... Engine as drive source for compressor and drive source for supercharger, M ... Electric motor as drive source for supercharger which constitutes supercharging pressure changing means .

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Tomoji Tarutani             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Naoto Kawamura             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Kenji Mochizuki             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Akiaki Wang             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Tetsuyuki Shintoku             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Kazuhiko Yokota             Nagoya Kogyocho, Showa-ku, Nagoya City, Aichi Prefecture             Inside college F-term (reference) 3H003 AA03 AB07 AC03 CC00 CF00                 3H029 AA02 AA04 AA06 AB03 BB31                 3H045 AA04 AA10 AA27 BA31 CA02                       DA09 DA12                 3H076 AA06 BB21 BB38 CC12 CC20                       CC81

Claims (15)

[Claims] 1. A refrigerating cycle, wherein a compression mechanism is operated by driving a drive source for a compressor, thereby sucking a refrigerant gas into the compression chamber, compressing the refrigerant gas in the compression chamber, and compressed. In a compressor configured to discharge refrigerant gas from a compression chamber, a supercharger for increasing the mass flow rate of the refrigerant gas drawn into the compression chamber, and a supercharger for driving the supercharger. A suction drive device for a compressor, wherein the supercharger is of a pressure wave type. 2. The low pressure refrigerant gas introducing portion for introducing the low pressure refrigerant gas in the suction pressure region of the refrigeration cycle,
A supercharging refrigerant introduction part for introducing a supercharging refrigerant in a discharge pressure region or a liquid refrigerant region of a refrigeration cycle, a cell for compressing the low pressure refrigerant gas by the supercharging refrigerant, and a compressed low pressure refrigerant gas The suction promoting device for a compressor according to claim 1, further comprising a low-pressure refrigerant gas lead-out portion that leads out from the cell to a compression chamber of the compressor. 3. The supercharger has a supercharging refrigerant lead-out portion for leading the supercharging refrigerant after compressing the low-pressure refrigerant gas from the cell to a suction pressure region of a refrigeration cycle.
A suction promoting device for a compressor according to. 4. A refrigeration cycle, wherein a compression mechanism is operated by driving a drive source for a compressor, thereby sucking a refrigerant gas into the compression chamber, compressing the refrigerant gas in the compression chamber, and compressed. In a compressor configured to discharge refrigerant gas from a compression chamber, a supercharger for increasing the mass flow rate of the refrigerant gas drawn into the compression chamber, and a supercharger for driving the supercharger. And a drive source for the supercharger, wherein the supercharger is of a positive displacement type. 5. The suction promoting device for a compressor according to claim 1, wherein the supercharger is mounted in a housing that houses a compression mechanism. 6. The suction promoting device for a compressor according to claim 1, wherein the supercharger is arranged independently of a housing that houses a compression mechanism. 7. The suction promoting device for a compressor according to claim 1, wherein the compressor drive source also serves as a supercharger drive source. 8. The suction enhancer for a compressor according to claim 1, wherein the drive source for the supercharger is provided separately from the drive source for the compressor. 9. In the compression mechanism, the piston is reciprocated by the rotation of a drive shaft supported by the housing, thereby sucking and compressing the refrigerant gas from the suction pressure region to the compression chamber via the suction valve mechanism. The refrigerant gas is compressed in the room, and the compressed refrigerant gas is discharged to the discharge pressure region. The suction valve mechanism has a compression chamber and a suction pressure region that rotate in synchronization with the drive shaft. A rotary valve capable of opening and closing the gas passage between the two is used.
A suction promoting device for a compressor according to any one of 1. 10. The compressor drive source also serves as a supercharger drive source, and the supercharger is mounted in a housing. The rotary member, drive shaft, and rotary valve of the supercharger are The suction promoting device for a compressor according to claim 9, wherein the suction promoting device is arranged on the same axis and is integrated. 11. The supercharger is a pressure wave type having a discharge pressure region of a refrigeration cycle as a high pressure source, and the rotating member is a rotor having a plurality of cells around its rotation axis. A suction promoting device for a compressor according to. 12. The supercharger is a pressure wave type using a liquid refrigerant region of a refrigeration cycle as a high pressure source, and the rotating member is a rotor having a plurality of cells around its rotation axis. A suction promoting device for a compressor according to. 13. The rotary valve and the rotor of the supercharger form a slide bearing surface with their outer peripheral surface and the inner peripheral surface of the housing of the compressor slid on the outer peripheral surface, and the drive shaft is a rotary bearing. The suction promoting device for a compressor according to claim 11 or 12, which is rotatably supported by the housing via a valve and a rotor. 14. The supercharger comprising: the suction accelerating device according to any one of claims 1 to 13; and supercharging pressure changing means capable of changing the supercharging pressure of the supercharger. A compressor control device, wherein the volumetric efficiency of the compressor can be controlled by adjusting the supercharging pressure of the compressor. 15. The supercharger drive source is provided separately from the compressor drive source, and the supercharging pressure changing means includes a supercharger drive source and a supercharger drive source. 15. The compressor control device according to claim 14, further comprising supercharging pressure control means for controlling the supercharging pressure of the supercharger by adjusting the output.