JPS58152192A - Oscillating rotary compressor - Google Patents

Abstract

PURPOSE:To increase the discharge rate of an oscillating rotary compressor and to enhance the discharging efficiency of the same,by disposing flaps in a housing, and oscillating the flaps within a predetermined angle of rotation. CONSTITUTION:V-shaped partition walls 16A, 16B are disposed at symmetrical positions in a housing 10, so that sector-shaped work chambers 17A, 17B are defined in the housing 10. Suction ports 20A, 21A and discharge ports 20B, 21B are formed in the V-shaped portition wall 16A in side-by-side relationship with each other. Similarly, suction ports and discharge ports are also formed in the other partition wall 16B in side-by-side relationship. With such an arrangement, the flaps 15A, 15B are oscillated in the work chambers 17A, 17B within a predetermined angle theta of rotation between the partition walls 16A and 16B.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is directed to an oscillating compressor in which a flap reciprocates over a certain distance.

In general, a vane-lid compressor has a rotor 3 attached to a rotating shaft 2 eccentric from the center inside a circular housing 1, as shown in FIG. 4 are arranged to be freely expandable and contractible, and as the rotor 3 rotates, the plate 74 slides in and out of the circumferential wall IAK of the housing 1, and the working chamber 5 formed between the vanes 1 and The gas is expanded by the rotation of 3, and at this time, the gas sucked in from the suction port 6 in the expansion stroke is forced to be discharged from the discharge lower in the contraction stroke. (For example, 1 Japan Society of Mechanical Engineers, published June 1960.
Mechanical Engineering Handbook JP9-68) Note that the vane 4 protrudes outward due to centrifugal force.

By interposing a spring at the bottom or by guiding a part of the discharge pressure, the circumferential wall of the no.
AK Close.

By the way, the rotor 3 allows the vane 4 to move in and out at 9vI.

Due to the relationship, the diameter cannot be made so small, and the volume of the connecting l is -l.

Since the rotor 3 occupies a large proportion, the volume change portion (corresponding to the stroke volume) that is related to the compressor discharge amount becomes small. 1 Uzing 1 [Must be expanded! There was.

However, when pressure is applied like this, Pei 74 and 71 Uzing 1
The larger the seal length of the sliding contact portion with the circumferential wall IA), the more likely leakage of compressed gas (fluid) occurs, making it difficult to obtain a pump with high efficiency.

In addition, Pei 74 always has 9t-ml in and out for April 3.
), there was a problem in terms of durability as there was a lot of wear and tear.

The present invention was proposed for the ninth time to solve such problems, and consists of disposing a flap having a coaxial center of rotation t inside a housing having a circular cross section t.

By reciprocating 7 laps within a predetermined rotation angle range, the fluid is sucked into and discharged from the fan-shaped working chamber, and although it is a shed, the oscillating type has a large discharge flow rate and high discharge efficiency. The purpose is to provide a compressor company.

Hereinafter, a description will be given based on drawings showing examples of the present invention.

As shown in FIG. 2 to FIG.
A and 11B are hermetically tightened by tightening bolts 12.

The compressor drive shaft 13 is located in the center of the housing 10, and the bearing 14 of the side housing IIA, 11f3 is located in the center of the housing 10.
The drive shaft 13 is rotatably supported through a mechanism, and flaps 15A and 15B are integrally attached to the drive shaft 13.

On the other hand, inside the housing 10, in this embodiment, there are 7
Shape partition walls 16A and 16B are arranged symmetrically to form fan-shaped working chambers 17A and 17B'i in the housing circle.

And the 7-shaped partition wall 16A has suction boats 20A, 2
1A and the discharge bow) 20B, 21B are opened in parallel, and the suction bow) 22A is similarly opened in the other partition wall 16B.
, 23A and the discharge boats 22B, 23B are opened in parallel.

The suction port 25 of the housing 10 has a partition wall 1.
At 6A@, the suction boats 20A and 21A, which communicate with the respective working chambers 17A and 17B, are opened.

Similarly, the discharge ports 20B and 21B, which communicate with the 1-operation 1!17A and 17B, are opened in the discharge port 26 as well.

Similarly, one operation m17 is applied to the suction port 25 of the partition wall 16B@.
A, 17BK continuous suction bow) 22A.

23 Air works just as well! The discharge boats 22B and 23111 communicate with the discharge ports 26, which communicate with the discharge ports 17A and 17B.

The flaps 15A, 15B are connected to the working chambers 17A, 1.
7B, each suction port 20 is rotated within a predetermined rotation angle θ between the partition walls 16A and 168
A, 21A, 22A.

Operates from 23A! The gas (fluid) injected into 17A and 17B is discharged respectively) 20B, 21B.

It is discharged from 22B and 23B.

The suction boats 20A, 21A, 22A, 23A and the discharge boats 20B, 21B, 22B, 23fl are each equipped with a check valve, but in this embodiment, a reed valve with a simple structure is adopted.

The flaps 15A and 15B are fixed to the drive shaft 13, extend integrally from the next boss portion 28, and come into sliding contact with the inner circumferential surface of the housing 10, and are similarly attached to the housings IIA and IIB.
1 working chamber 17A, 17
Change the volume of B.

A swing arm 29 is attached to the protruding end of the first drive shaft 13 in order to cause the drive shaft 13 to reciprocate within the predetermined rotation angle range 0, and a connecting rod 3 is attached to this arm 29.
0', a crank arm 31 is similarly connected to the other end of the connecting rod 30, and is rotated by a power source such as a Clamfer 531 gold motor.
The arm 29 is designed to make a rocking motion.

Next, to explain the working pressure, 1 of the link arm 31
As the swing arm 29 rotates, the swing arm 29 moves the drive shaft 13 within a predetermined angle range θ, that is, the flaps 15A and 15B are defined by the partition walls 16A and 16B, and the swing arm 29 moves the drive shaft 13 into a nine fan-shaped operation m17.
A and 17B P31! Rotate it back and forth with Is.

When the flaps 15A and 15B start rotating clockwise from the state shown in FIG. 4, they are compressed by the flaps 15A and 15.1! The gas 17A is sent pt5 to the discharge boat 22B of the discharge port 26, and at the same time, the gas in the working chamber 17B is also sent to the other discharge port 21B of the discharge port 26.

At this time, on the back side of the flaps 15A and 15B, the volume expands as the flaps 15A and 15B rotate, so gas is sucked in from the suction ports 20A and 23A of the inlet 25.25, respectively.

When the flaps 15A and 15B rotate by an angle θ, both the discharge stroke and the suction stroke due to the clockwise rotation are completed, and then the drive shaft 13 starts to reverse.

Next, gas is sucked in and discharged from the other suction boat 21A and discharge boat 23B, which are parallel to the 22 suction boats and the discharge port 20B, through the suction port 25. This is done through the discharge port 26, and the suction and discharge actions are performed in the same way during the return stroke of the flaps 15A and 15B.

In other words, flaps 15A and 15B operate after one reciprocation! 17A and 17B, which causes the compressor pressurization (discharge 9 action is obtained.

In addition, since compressed gas passes through the discharge port 26 compared to the suction port 25, its capacity (effective area) may be made smaller.

Furthermore, if the axial length and radial length of the flap 15A (15B) are approximately equal, one working chamber 17A (17B)
) The length of the sealing part (sliding part) required to obtain the same volume (1) can be minimized, and a more efficient product with less leakage can be obtained.

Also, if the flaps 15A and 15B are made of lightweight synthetic resin, it will be easier to lubricate the circumference of the housing.

Processability also improves.

As described above, according to the present invention, since the flap is rotated back and forth within the fan-shaped operating chamber formed in the circular portion of the housing, it is possible to take an extremely large stroke volume considering the external dimensions of the housing. In addition, the length of the sealing portion can be reduced, resulting in a compressor with high volumetric efficiency and low leakage flow rate.

In addition, the structure is simple and the movement of the operating parts is simple.
There is less worry about breakdowns, and durability is increased.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a conventional vane compressor. FIG. 2 is a front view showing an embodiment of the present invention, and FIG. 3 is A-All! of FIG. 11-, FIG. 4 is a sectional view taken along the line B--B in FIG. 3, and FIGS. 5 and 6 are front views of the boat portion, respectively. 10.11A, 11B...Housing, 13...Drive shaft, 15A, 15B...Flap, 16A, 16B
...Partition wall, 17A, 17B--Made 111! , 20
A. 21A, 22A, 23A... suction bow), 20B. 21B, 22&, 23B...discharge bow), 25=...
Suction 0.26...Discharge 0.29...Swing arm. 30...Connecting rod, 31...Crank arm. Patent applicant Nissan Motor Co., Ltd.

Claims (1)

[Claims] The inside of the housing having a circular cross section is divided into two partition walls for the working chamber, and a circular section is provided at the center of the shaft and extends to the vicinity of the peripheral wall surface of the working chamber. A swinging type characterized in that a flap is attached, and a crank mechanism is provided to fully reverse the drive shaft so that the flap reciprocates between the partition walls, and the partition wall has a fluid suction port and a fluid discharge port fully opened. compressor.