JPH01155095A - 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 lubricating oil under pressure at the time of its starting. CONSTITUTION:At the time of operation starting of a vane type rotary compressor 2, a pressure value of a high pressure chamber 50 is low, and it becomes less than the setting pressure value, whereby a pressure switch of a pressure-feed means 64 is closed. Consequently, a solenoid 72 is energized with current, pushing a piston forward, and lubricating oil is fed to each vane chamber from a pressure-feed chamber 66 by a connecting groove 62 via a sixth lubricating oil passage 54b branched off from a second lubricating oil passage 54. Accordingly, a vane 8 can be fully pressed to an inner circumferential surface 4a of a cylinder 4.

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 at least one point, and is in full contact with the inner circumferential surface within a groove formed in the outer circumferential surface in a substantially radial direction with respect to the center of the rotor. A vane is provided so that it 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 preferable for the compressor or 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. 61-11.8583, the fluid in the working chamber is supplied to the vane chamber at the start of startup, while the lubricating oil in the high pressure chamber is supplied during steady operation when the pressure in the high pressure chamber is high. Some press the vane against the inner peripheral surface of the cylinder by supplying the vane to the vane chamber.

However, since the pressure in the working chamber is not very high at the start of startup, the method 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, the vane type rotary compressor There are disadvantages in that the vane may be sufficiently pressed against the inner circumferential surface of the cylinder at the start of startup, and the fluid may not be compressed well.

[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, lubricating oil of the vane-type rotary compressor is transferred to the vane base in the rotor groove when starting the vane-type rotary compressor. It is characterized by providing a pressure-feeding means for force-feeding to a vane chamber partitioned on the side.

[Effect]

According to the configuration of the present invention, the vane is pushed toward the inner circumferential surface of the cylinder by forcing the lubricating oil into the vane chamber at the start of startup of the vane type rotary compressor by the pressure feeding means. As a result, the vane is sufficiently pressed against the inner circumferential surface of the cylinder at the start of 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, the shaft portion 16 of the rotor 6 is provided with a boot IJ at the outer end.
22, an electromagnetic clutch mechanism 24 is provided to intermittent transmission of driving force. This electromagnetic clutch mechanism 24 has a solenoid 26.

This solenoid 26 drives the vane type rotary compressor 2.
For example, it is connected to the power source 3o via an activation switch 28 of 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 expands and contracts in the rotational direction of the rotor 6 (in the 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 provided at a front position and a rear position, respectively, in the rotor concave rotation direction of the portion of the cylinder 4 that contacts the rotor 6. 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 enclosure 42 is provided with a fluid inlet port 44 and an outlet boat 46. Said electromagnetic cladding mechanism 2
When the solenoid 26 of the cylinder 4 is energized to connect the shaft portion 16 and the pulley 22 and 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. The working chamber 32 is moved in the rotor rotational direction while expanding and contracting. 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 through the suction port 34 and compressed, and then pushes the discharge valve 40 from the discharge port 36. It is opened and discharged. 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 side plate 10 on the side of the oil storage chamber 52 is provided with a first lubricating oil passage 54a whose starting end opens at a lubricating oil port 56 provided in the oil storage chamber 52, and a terminal end of this first lubricating oil passage 54a is provided with a second lubricating oil passage 54a. The lubricating oil passage 54b and the third lubricating oil passage 54c are branched and provided. The second lubricating oil passage 54b is provided in communication with an oil groove 58 provided around the shaft portion 14. The third lubricating oil passage 54C is connected to the oil storage chamber 52 via a fourth lubricating oil passage 54d provided in the cylinder 4.
This fifth lubricating oil passage 54e is provided in communication with an oil groove 60 provided around the shaft portion 16. In addition, the side plate 1
0, the second lubricating oil passage 54b to the sixth lubricating oil passage 54
f is branched and provided. The sixth lubricating oil passage 54f is provided in communication with each of the vane chambers 20 through an annular communication groove 62 provided on the side surface of the rotor 6 at a portion in contact with the shaft portion 14.

Thereby, the lubricating oil stored in the oil storage chamber 52 is transferred to the oil grooves 58 and 6 by the first to fifth lubricating oil passages 54a to 54e.
0 to lubricate the sliding parts between the respective shaft parts 14 and 16 and the side plates 10 and 12, and also to each vane through communication 462 through a sixth lubricating oil passage 54f branched from the second lubricating oil passage 54b. It is supplied to the chamber 20 and lubricates the sliding portion between the groove portion 18 and the vane 8.

A first lubricating oil passage 5 that supplies lubricating oil to this vane chamber 20
In the middle of 4a, a pressure feeding means 64 is provided for pumping lubricating oil to the vane chamber 20 when the vane type rotary compressor 2 starts to be started. This pressure-feeding means 64 includes a pressure-feeding chamber 66 formed by expanding a part of the first lubricating oil passage 54a, a piston 68 in this pressure-feeding chamber 66, and a Rondo door 0 connected to this piston 68.
Then, the solenoid 72 becomes energized by being energized to push the piston 68 from its original position via this Ron door 0.
A return spring 74 returns the piston 68 to its original position, and a pressure value in the high pressure chamber 50 is adjusted to a set pressure, for example, in order to energize the solenoid 72 and bring it into an energized state at the start of starting the vane type rotary compressor 2. It has a pressure cassothiae 6 which closes when the pressure is less than the value. The pressure gas isothia 6 is connected to a power source 30 via an operation switch 28 for driving and stopping the vane-type rotary compressor 2. Incidentally, the reference numeral 78 denotes the first portion of the pressure feeding chamber 66 on the oil storage chamber 52 side.
This is a constricted portion provided in the lubricating oil passage 54a.

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 the expansion and contraction of the working chamber 32, fluid such as refrigerant gas that has flowed into the suction passage 38 from the artificial boat 44 is sucked into the working chamber 32 from the suction port 34 and compressed, and then passes through the old outlet valve 40 from the discharge port 36. It is pushed open and discharged into the high pressure chamber 50 inside the envelope 42 .

At the start of the vane type rotary compressor 2, the pressure value in the high pressure chamber 50 is low and less than the set pressure value, and the pressure gas isothia 6 of the pressure feeding means 64 is closed. As a result, when the actuation switch 28 is closed in order to drive the vane type rotary compressor 2, the solenoid 72 is energized and energized by the closing of the pressure switch 76, and the piston in the pressure feeding chamber 66 is 68 from its original position. By pushing this piston 68, the pressure feeding chamber 6
The lubricating oil in 6 is compressed and fed from the first lubricating oil passage 54a toward the second and third lubricating oil passages 54b and 54C.

At this time, the first lubricating oil passage 54a on the oil storage chamber 52 side is closed by the piston 6B that is provided with the throttle portion 78 and is pushed forward, so that the compressed lubricating oil is not fed to the oil storage chamber 52 side. do not have.

The lubricating oil compressed and supplied from the pressure feeding chamber 66 is
Lubricating oil passage 54. A sixth lubricating oil passage 54 branched from b
is supplied to each vane chamber 20 via the communication groove 62 via f,
The inner peripheral surface 4a of the cylinder 4 acts as a back pressure on the vane 8.
push towards.

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. In addition, as in the past, the vane type rotary compressor 2
When starting the compressor 2, there is no need to increase the rotation speed to push the vane forward by centrifugal force and press the vane 8 against the inner circumferential surface 4a of the cylinder 4.
It is possible to save fuel for the prime mover such as the internal combustion engine that drives the engine. Furthermore, since the lubricating oil compressed and supplied from the pumping chamber 66 is supplied to the oil grooves 58 and 60 through the first to fifth lubricating oil passages 54a to 546, when starting the vane type rotary compressor 2, Each shaft part 14, 16 and side plate 10, 12
By being able to satisfactorily lubricate the sliding parts between the two parts, mechanical loss can be reduced.

When the compressed fluid is discharged into the high pressure chamber 50 within the envelope 42 and the pressure value of the high pressure chamber 50 becomes equal to or higher than the set pressure value, the pressure switch 76 opens. When the pressure gas isothiae 6 is opened, the trenoid 72 is de-energized and becomes a non-excited state, and the piston 68 in the pressure feeding chamber 66 is returned to its original position by the return spring 74. This results in
In a steady operating state, lubricating oil is supplied by the pressure within the high pressure chamber 50 to lubricate each part.

〔Effect of the invention〕

As described above, according to the present invention, the vane is pushed toward the inner circumferential surface of the cylinder by force-feeding lubricating oil into the vane chamber by the pressure-feeding means at the start of startup of the vane-type rotary compressor.

Thereby, at the start of the vane type rotary compressor, the vane can be sufficiently pressed against the inner peripheral surface of the cylinder, and the fluid can be favorably compressed. In addition, unlike conventional vane-type rotary compressors, there is no need to push the vanes forward by centrifugal force and increase the rotation speed to press the vanes against the inner peripheral surface of the cylinder at the initial stage of startup of the vane-type rotary compressor. It is possible to save fuel for the prime mover such as the internal combustion engine that drives the compressor, and it is also possible to pump lubricating oil to each sliding part, so that each sliding part is It can be well lubricated.

[Brief Description of the Drawings] Figures 1 and 2 show an embodiment of the present invention, with Figure 1 being a partially cutaway sectional view of a vane type rotary compressor, and Figure 2 being a partially cutaway sectional view of a vane type rotary compressor. FIG. 3 is a cross-sectional view of the rotor portion of the machine. In the figure, 2 is a vane type rotary compressor, 4 is a cylinder,
6 is a rotor, 8 is a vane, 18 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, 52 is an oil storage chamber, and 54a~
54f are the first to sixth lubricating oil passages, 62 are communication grooves, and 6
4 is a pressure feeding means, 66 is a pressure feeding chamber, 68 is a piston, 70 is a rond, 72 is a solenoid, 74 is a return spring, 76 is a pressure switch, and 78 is a constriction portion. 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 is partitioned, at the start of startup of the vane-type rotary compressor, the lubricating oil of the vane-type rotary compressor is forced into a vane chamber that is partitioned and formed on the vane base side in the rotor groove. A vane type rotary compressor characterized by being provided with means.