JPH01155096A - Vane type rotary compressor - Google Patents

Abstract

PURPOSE:To compress a fluid so favorably at the time of operation starting by feeding a vane chamber, to be partitively formed at the vane base side, with a high pressure fluid stored at the time of its starting. CONSTITUTION:At the time of driving a vane type rotary compressor 2, part of a high pressure fluid being discharged to a high pressure chamber 50 by an operating chamber 32 pushes a check valve 72 open and flows into a storage chamber 74 of a first connecting passage 68a from a fluid intake 66. When an actuating switch 28 is closed at the time of starting the vane type rotary compressor 2, a solenoid 78 is energized with current by closing a pressure switch 80 and it comes into a state of being excited, whereby a valve body 76 is opened and a second connecting passage 68b is interconnected. With this constitution, the high pressure fluid inside the storage chamber 74 is fed to each vane chamber from this second connecting passage 68b via a ring connecting groove 70 at the side of a rotor 6.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a vane type rotary compressor, and particularly to a vane type rotary compressor that can sufficiently press the vane against the inner circumferential surface of a cylinder at the start of startup of the vane type rotary compressor. The present invention relates to a vane-type rotary compressor that can compress fluid well.

[Conventional technology]

Rotary compressors include rolling piston type, slide vane type, and turbo type. Among these various types of rotary compressors, the vane type rotary compressor has a cylindrical rotor rotatably provided within a cylinder. The rotor rotates with its outer circumferential surface in contact with the inner circumferential surface of the cylinder at least at one point through a plate, and the inner circumferential surface is formed in a groove formed in the outer circumferential surface in a substantially radial direction with respect to the center of the rotor. There are vanes that can appear and appear.

As a result, the vane type rotary compressor partitions a working chamber between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotor as the rotor rotates, and which moves while expanding and contracting in the rotor rotational direction by the vanes. It sucks in fluid, compresses it, and then discharges it. This vane type rotary compressor is used, for example, in an air conditioner that compresses and supplies refrigerant gas or the like.

[Problems to be Solved by the Invention] Incidentally, in a vane type rotary compressor, in order to define a working chamber that moves while expanding and contracting in the rotor rotational direction as described above, a rotor that rotates in a cylinder has a groove inside the rotor. A vane is provided so that it can appear. This vane is pushed forward by centrifugal force due to rotation of the rotor, back pressure of high-pressure fluid in a high-pressure chamber introduced into a vane chamber partitioned on the vane base side in the groove, and pressed against the inner circumferential surface of the cylinder. This compresses the fluid.

However, at the start of the vane-type rotary compressor, the pressure of the fluid discharged into the high-pressure chamber is low, so the vanes cannot be sufficiently pushed forward. Further, the vane is stuck in the groove by lubricating oil at the start of startup. For this reason,
The rotational speed is increased to generate a large centrifugal force, and this centrifugal force pushes the vanes forward. However, increasing the rotational speed at the start of startup is not desirable for the compressor or for the prime mover such as the internal combustion engine that drives the compressor.

Therefore, for example, as disclosed in Japanese Patent Application Laid-Open No. 61-118583, fluid in the working chamber is supplied to the vane chamber at the start of startup, while lubricating oil in the high pressure chamber is supplied to the vane chamber during steady operation when the pressure in the high pressure chamber is high. There is one that presses the vane against the inner peripheral surface of the cylinder by supplying it to the chamber.

However, since the pressure in the working chamber is not very high at the start of startup, the technique disclosed in this publication has the disadvantage that the vane cannot be sufficiently pressed against the inner circumferential surface of the cylinder. As a result, when starting the vane type rotary compressor, the vane cannot be sufficiently pressed against the inner circumferential surface of the cylinder, resulting in an inconvenience that the fluid cannot be compressed satisfactorily.

[Purpose of the invention]

Therefore, an object of the present invention is to realize a vane-type rotary compressor that can sufficiently press the vanes against the inner circumferential surface of the cylinder at the start of the vane-type rotary compressor, and can compress the fluid well. be.

[Means for solving problems]

In order to achieve this object, the present invention utilizes a cylinder, a rotor rotatably provided in the cylinder, and vanes retractably provided in a groove formed substantially radially with respect to the center of the rotor. In a vane-type rotary compressor that partitions and forms a working chamber that moves while expanding and contracting in the rotational direction of the rotor, a part of the high-pressure fluid discharged from the working chamber is stored when the vane-type rotary compressor is driven, and the vane The present invention is characterized in that a supply means is provided for supplying the stored high-pressure fluid to a vane chamber partitioned and formed on the vane base side in the rotor groove portion at the start of startup of the mold rotary compressor.

[Effect]

According to the configuration of the present invention, the supply means stores a part of the high-pressure fluid discharged from the working chamber when the vane-type rotary compressor is driven, and the stored high-pressure fluid is stored when the vane-type rotary compressor starts to be started. of fluid is supplied to the vane chamber of the rotor. Thereby, the vane can be sufficiently pressed against the inner circumferential surface of the cylinder at the time of starting the vane type rotary compressor.

〔Example〕

Next, embodiments of the present invention will be described in detail based on the drawings.

Figures 1 and 2 show an embodiment of this invention.

In the figure, 2 is a vane type rotary compressor, 4 is a cylinder,
6 is a rotor, 8 is a vane, and 10 and 12 are side plates. The cylinder 4 has an elliptical inner peripheral surface 4a inside,
Two side plates 10 and 12 are fixed on both sides.

The rotor 6 has a circular outer peripheral surface 6a and is rotatably provided within the inner peripheral surface 4a of the cylinder 4. This rotor 6 has an outer circumferential surface 6a connected to an inner circumferential surface 4 of the cylinder 4.
In this example, at least one location in a,
The rotor 6 is rotated by shaft portions 14 and 16 on both sides so as to rotate while contacting the inner circumferential surface 4a of the cylinder 4 at two points.
It is supported by two side plates 10 and 12. A plurality of grooves 18 are formed in the outer peripheral surface 6a of the rotor 6 in substantially radial directions with respect to the center. The vane 8 is provided in the groove 18 so as to be retractable toward the inner circumferential surface 4a of the cylinder 4, and a vane chamber 20 is defined within the groove 18 on the side of the base 8a of the vane 8.

Further, a pulley 22 at the outer end is attached to the shaft portion 16 of the rotor 6.
An electromagnetic clutch mechanism 24 that intermittents transmission of driving force between
is provided. This electromagnetic clutch mechanism 24 has a solenoid 26.

This solenoid 26 drives the vane type rotary compressor 2.
It is connected to a power source 30 via an activation switch 28 of, for example, an air conditioner (not shown). As a result, when the actuation switch 28 is closed and the solenoid 26 is energized and energized, the shaft portion 16 and the pulley 22 are connected to transmit the driving force of a prime mover such as an internal combustion engine (not shown). On the other hand, when the actuation switch 28 is opened to cut off the energization to the solenoid 26 and make it into a non-excited state, the shaft portion 16 and the pulley 22 are separated and the transmission of driving force is cut off.

These cylinder 4, rotor 6, vane 8 and side plate 10.
12 define a working chamber 32 that moves while expanding and contracting in the rotational direction of the rotor 6 (direction of arrow A). This working chamber 32 is provided with an inlet port 34 and a discharge port 36 which are open thereto. The suction port 34 and the discharge port 36 are connected to the cylinder 4.
The rotor 6 is provided at a front position and a rear position in the rotational direction of the rotor in contact with the rotor 6, respectively. A suction passage 38 is provided in communication with the suction port 34, and a discharge valve 40 for preventing backflow is provided in the discharge port 36.

Furthermore, the cylinder 4 is covered by a covering body 42 . The envelope 42 is provided with a fluid inlet port 44 and an outlet port 46. The electromagnetic clutch mechanism 2
The solenoid 26 of No. 4 is energized to connect the shaft portion 16 and the boot U 22.
When the rotor 6 is rotated by transmitting the driving force, the vane 8 slides while contacting the elliptical inner peripheral surface 4a of the cylinder 4, expanding and contracting the working chamber 32, and rotating the rotor in the rotor rotation direction. move it to By expanding and contracting this working chamber 32,
A fluid such as refrigerant gas that has flowed into the suction passage 38 from the inlet port 44 is sucked into the working chamber 32 from the suction port 34 and compressed, and then is discharged from the discharge port 36 by pushing open the discharge valve 40 . The fluid discharged from the discharge port 36 is separated from lubricating oil by an oil separator 48 and discharged into a high pressure chamber 50, which is a discharge space within the envelope 42, and is then discharged from the outlet boat 46 to a desired site, such as an air conditioner. Supplied to equipment capacitors, etc.

The lubricating oil separated by the oil separator 48 is transferred to the high pressure chamber 5.
The lubricating oil is stored in the oil storage chamber 52 at the bottom of the 0, and is supplied to each sliding portion through the lubricating oil passage 54. That is, the starting end opens at a lubricating oil port 56 provided in the oil storage chamber 52, and branches into the shaft portion 14.
A lubricating oil passage 54 is provided which ends in an oil groove 58 provided around the shaft portion 16 and an oil groove 60 provided around the shaft portion 16 . Through this lubricating oil passage 54, the lubricating oil stored in the oil storage chamber 52 is supplied to the oil grooves 58 and 60, and lubricates each sliding portion such as the shaft portions 14 and 16 and the vane 8.

This vane type rotary compressor 2 includes a vane type rotary compressor Im.
, stores a part of the high-pressure fluid discharged from the working chamber 32 to the high-pressure chamber 50 when the vane-type rotary compressor 2 is driven, and supplies the stored high-pressure fluid to the vane chamber 20 when the vane-type rotary compressor 2 starts to start. A supply means 62 is provided. That is, a first communication passage 68a whose starting end opens at a fluid intake port 66 provided in a holder 64 that holds the oil separator 48;
The vane chamber 20 has a communication start end on the terminal end side of the communication passage 68a.
The side plate 1 has a terminal opening in an annular communication groove 70 provided on the side surface of the rotor 6 at a portion where the shaft portion 14 contacts, in order to communicate with each other.
A communication passage 6 consisting of a second communication passage 68b provided at
8 will be provided.

The first communication passage 68a of the communication passage 68 is provided with a check valve 72 and a storage chamber 74 sequentially from the fluid intake port 66 side to allow high pressure fluid to flow in from the high pressure chamber 50. The second communication passage 68b includes the second communication passage 6
A valve body 76 is provided to disconnect communication from the valve 8b.

A solenoid 78 is provided, which becomes an energized state when energized to open the valve body 76, and becomes a de-energized state when the energization is cut off to close the valve body 76,
When the vane type rotary compressor 2 is driven, the solenoid 78 is de-energized and becomes a non-excited state, and when the vane type rotary compressor 2 starts to be started, the solenoid 78 is energized and placed in an energized state. A pressure switch 80 is provided which opens when the pressure value of the high pressure chamber 50 is equal to or higher than the set pressure value and closes when the pressure value of the high pressure chamber 50 is less than the set pressure value. This pressure switch 80 is connected to the power source 30 via the operation switch 28 that drives and stops the vane type rotary compressor 2.

Next, the effect will be explained.

When the operating switch 28 is closed in order to drive the vane type rotary compressor 2, the solenoid 26 of the electromagnetic clutch mechanism 24 is energized and excited, and the shaft portion 16 and the pulley 2 are energized.
2 to transmit the driving force of a prime mover such as an internal combustion engine (not shown). This driving force causes the rotor 6 to start rotating, and the vanes 8 slide in contact with the elliptical inner peripheral surface 4a of the cylinder 4, expanding and contracting the working chamber 32 while moving in the rotor rotational direction. Due to this expansion and contraction of the working chamber 32, fluid such as refrigerant gas that has flowed into the suction passage 38 from the inlet boat 44 is sucked into the working chamber 32 from the suction port 34 and compressed, and then pushes the discharge valve 40 from the discharge port 36. It is opened and discharged into the high pressure chamber 50 inside the envelope 42.

When the vane type rotary compressor 2 is driven, the working chamber 32
A portion of the higher pressure fluid discharged into the higher pressure chamber 50 pushes open the check valve 72 from the fluid intake port 66 and flows into the first communication passage 68.
It flows into the storage chamber 74 of a.

At this time, the pressure value in the high pressure chamber 50 is high due to the high pressure fluid discharged from the working chamber 32 and exceeds the set pressure value, and the pressure switch 80 of the supply means 62 is opened.

When the pressure switch 80 is opened, the solenoid 78 is de-energized and becomes a non-energized state, and the valve body 76 is closed to block the second communication passage 68b. Therefore, when the vane-type rotary compressor 2 is driven, a part of the high-pressure fluid discharged from the working chamber 32 to the high-pressure chamber 50 is stored in the storage chamber 74 without being supplied to the vane chamber 20. .

After the drive of the vane type rotary compressor 2 is stopped, the pressure value in the high pressure chamber 50 is low and less than the set pressure value, and the pressure switch 80 of the supply means 62 is closed. However, since the actuation switch 28 is open, the solenoid 78 is de-energized and is de-energized, closing the valve body 76 and blocking the second communication passage 68b, so that high-pressure fluid flows into the vane chamber. 20 will not be supplied.

At the start of the vane type rotary compression m2, the activation switch 2
When the pressure switch 80 is closed, the solenoid 78 is energized and energized by closing the pressure switch 80 as described above, and the valve body 76 is opened and the second communication passage 68b is communicated.

As a result, the high-pressure fluid in the storage chamber 74 is supplied from the second communication passage 68b to each vane chamber 20 via the annular communication groove 70 on the side surface of the rotor 6, and acts as back pressure on the vane 8, causing the cylinder 4 is pushed toward the inner circumferential surface 4a.

Therefore, at the start of the vane type rotary compressor 2, the vane 8 can be sufficiently pressed against the inner circumferential surface 4a of the cylinder 4, and thereby the fluid can be compressed well.

When the compressed high-pressure fluid is discharged into the high-pressure chamber 50 and the pressure value of the high-pressure chamber 50 becomes equal to or higher than the set pressure value,
Pressure switch 80 is opened. By opening the pressure switch 80, the solenoid 78 is de-energized and becomes de-energized, and the valve body 76 is closed and the second communication passage 68b is closed.
cut off.

Therefore, when the vane type rotary compressor 2 is driven, the storage chamber 7
4, a part of the high pressure fluid discharged from the working chamber 32 to the high pressure chamber 50 is stored without being supplied to the vane chamber 20. The high-pressure fluid stored in this storage chamber 74 is supplied to the vane chamber 20 as described above at the start of the next startup, and acts as a back pressure on the vane 8, causing the inner circumferential surface of the cylinder 4 to
a, the vane 8 is sufficiently pressed against the inner circumferential surface 4a of the cylinder 4, thereby compressing the fluid well.

In this way, the supply means 62 stores a part of the high-pressure fluid discharged from the working chamber 32 when the vane-type rotary compressor 2 is driven, and also stores a part of the high-pressure fluid discharged from the working chamber 32 when the vane-type rotary compressor 2 is started. By supplying this fluid to the vane chamber 20 of the rotor 6, the vane 8 can be sufficiently pressed against the inner circumferential surface 4a of the cylinder 4 at the start of the vane-type rotary compression a2. Can be compressed.

In addition, unlike conventional systems, there is no need to increase the rotational speed to push the vanes forward by centrifugal force and press the vanes 8 against the inner circumferential surface 4a of the cylinder 4 at the start of the vane-type rotary compressor 2. It is possible to save fuel in the compressor 2 and also in a prime mover such as an internal combustion engine that drives the compressor 2. Furthermore, only at the start of the vane type rotary compressor 2, high pressure fluid is supplied to the vane chamber 20 to press the vane 8 against the inner circumferential surface 4a of the cylinder 4, so that the vane 8 is moved inside the cylinder 4 during steady operation. It is possible to prevent the inconvenience of being excessively pressed against the peripheral surface 4a, and to reduce mechanical loss.

〔Effect of the invention〕

As described above, according to the present invention, the supply means stores a part of the high pressure fluid discharged from the working chamber when the vane type rotary compressor is driven, and also stores a part of the high pressure fluid discharged from the working chamber when the vane type rotary compressor is started. By supplying the high-pressure fluid to the vane chamber of the rotor, the vane can be sufficiently pressed against the inner circumferential surface of the cylinder at the start of the vane-type rotary compressor.

Therefore, at the start of the vane type rotary compressor, the vane can be sufficiently pressed against the inner circumferential surface of the cylinder, and the fluid can be compressed well. In addition, unlike conventional vane-type rotary compressors, there is no need to push the vanes forward by centrifugal force at the start of startup and increase the rotation speed to press the vanes against the inner peripheral surface of the cylinder. It is possible to achieve fuel savings in the prime mover such as the internal combustion engine that drives the compressor, and it is also possible to prevent the inconvenience of the vane being excessively pressed against the inner peripheral surface of the cylinder during steady operation, reducing mechanical loss. It is something that can be done.

[Brief explanation of the drawing]

Figures 1 and 2 show an embodiment of the present invention. Figure 1 is a partially cutaway sectional view of a vane type rotary compressor, and Figure 2 is a sectional view of the rotor portion of the vane type rotary compressor. It is. In the figure, 2 is a vane type concave compressor, 4 is a cylinder,
6 is a rotor, 8 is a vane, 1B is a groove, 20 is a vane chamber, 24 is an electromagnetic clutch mechanism, 28 is an actuation switch, 30
is a power source, 32 is an operating chamber, 34 is an intake port, 36 is a discharge port,
42 is an envelope, 50 is a high pressure chamber, 62 is a supply means, 64 is a holder, 66 is a fluid intake port, 68a is a first communication passage, 6
8b is a second communication passage, 70 is a communication groove, 72 is a check valve, 7
4 is a storage chamber, 76 is a valve body, 78 is a solenoid, and 80 is a pressure switch. Patent applicant: Suzuki Automobile Industry Co., Ltd. Agent: Yoshimi Nishigo, patent attorney

Claims (1)

[Claims] A working chamber that moves while expanding and contracting in the rotor rotational direction is formed by a cylinder, a rotor rotatably installed in the cylinder, and a vane retractably installed in a groove formed approximately radially to the center of the rotor. In a vane-type rotary compressor that forms compartments, a part of the high-pressure fluid discharged from the working chamber is stored when the vane-type rotary compressor is driven, and the stored high pressure is stored when the rotor-type rotary compressor starts to be started. A vane-type rotary compressor, characterized in that a supply means is provided for supplying the fluid to a vane chamber partitioned and formed on the vane base side within the rotor groove.