JPS60230501A - Rotary type high pressure gas rotation device - Google Patents

Abstract

PURPOSE:To obtain a simple construction and high efficiency gas rotation system for converting gas pressure energy to rotational energy by constructing the system with a pair of disc type stationary bases having a casing cam plane, a rotor provided with two sliding vanes, and a rotor guide frame. CONSTITUTION:During operation, a high pressure gas A flows alternately into four cylinders 13 partitioned with a casing cam plane 2, a rotor 3, and a rotor guide frame 8 through high pressure gas intake ports 10 provided at ends of flow-in passages 11 arranged positionally parting 90 deg. with each other overall to right and left stationary bases 1, 1. By the pressure of the high pressure gas A the plate surfaces of the alternately disposed sliding vanes 5 are pressed and the rotor 3 begins to rotate. With the rotation of the rotor 3, the sliding vanes 5 move leftwards corresponding to the cam displacement of the cam plane 2 and the cylinder chambers 13 which have hitherto been in small volume, are expanded successively, and the pressing force is increased. On the other hand, the low pressure gas within cylinder chambers 13b are exhausted through exhaust ducts 6, an annular duct 7, and a flow-out passage 12.

Description

[Detailed Description of the Invention] <Industrial Application Field> The present invention relates to a rotary-type high-pressure gas rotating device that converts the inflow pressure of high-pressure gas obtained from cold vs. fish pressure, air pressure, etc. into rotational energy. .

<Prior Art> In general, a pump motor called a gerotor, which is a combination of an outer rotor and an inner rotor, is known as a rotating device that rotates a rotor by introducing high-pressure fluid and discharging low-pressure fluid. However, since each of these axes has an eccentric shaft configuration, it is troublesome to manufacture, and the driving force is generated by a small pressing area of only the outer peripheral surface of the inner rotor body (thick and wide), so it is extremely large. It required high pressure fluid.

<Object of the Invention> In view of the above circumstances, an object of the present invention is to provide a highly efficient and simple rotating device in which the rotor and the casing are coaxially configured and the press is of a double-blade type.

<Structure of the Invention> The present invention includes a pair of disk-shaped fixed bases each having a casing cam surface having a sinusoidal developed cross section and having two convex and concave portions formed symmetrically so that the concave and convex portions face each other on opposing sides.
A rotor is mounted on a shaft in a constant 111 m of this opposing casing cam surface, and the side surface of the rotor is brought into contact with the convex part of the casing cam surface, and the recess space of the casing cam surface is used as a cylinder chamber, and the peripheral edge of the rotor A sliding vane with a length so that both ends are in contact with the opposing casing cam surface is installed in two places parallel to the axial direction, and a gas exhaust groove provided on the front surface of the sliding vane in the rotational direction and a gas exhaust groove of the rotor. An annular gas guide groove provided on the outer peripheral surface is communicated with the gas guide groove, and the gas guide groove is guided to a discharge hole of a rotor guide frame that is located between the fixed bases and covers the rotor, and is connected to four places on the left and right of the casing cam surface of the fixed bases. A high-pressure gas inlet is placed near each convex portion, and the inflow of high-pressure gas from the inlets arranged at alternate positions alternately presses the horizontally protruding sliding blades on the rotary side, causing the rotor to It is designed to rotate.

<Example> The present invention will be described below based on the drawings of the example.

1.1 is a pair of disk-shaped fixed bases having two successive waves of concavo-convex portions 2a, 2b, which cause cam displacement, on opposite side surfaces 1a, 1a, forming front cam-type casing cam surfaces 2, 2 having a sinusoidal cross section; In this case, the concave and convex waveforms of the casing cam surface 2.2 are arranged symmetrically so that the gap p between the casing cam surfaces 2.2 remains constant. Reference numeral 3 denotes a rotor that is slidably interposed between the fixed base 1.1, and the rotor 3 has a side surface 3a, and 3a is a convex portion 2b of the casing cam surface 2, 2.
, 2b, and has rotor stepped portions 3b, 3b in the central portion that match at least the width a of the concave portions 2a, 2a of the casing cam surfaces 2, 2, and the shaft 4 of the rotor 3. is mounted on the center of fixed bases 1, 1. Reference numeral 5 denotes a plate-shaped sliding blade having a length C that passes through the side surfaces 3a and 3a of the rotor 3 and has both ends reaching the outer casing cam surface 2.2. Symmetry 4') A dish-shaped gas exhaust groove 6 for low-pressure gas is arranged at two parallel locations and has an appropriate depth on the front surface of the vibrating blade 5 in the rotational direction. Further, this gas exhaust groove 6 portion faces a part of an annular gas guide groove 7 cut into the center of the outer circumferential surface 3C of the rotor 3, and communicates with the outside. Reference numeral 8 denotes a drum-shaped rotor guide frame interposed between the outer circumferential edges of the opposing fixed bases 1, 1, and the outer circumferential surface 3C of the rotor 3 is brought into sliding contact with the inner surface of the rotor guide frame 8, and is provided at the center of the inner surface. The annular receiving groove 9 and the annular gas guide groove 7 are made to match. , 10 are high-pressure gas intake ports arranged near the top of the casing cam of each fixed base 1, and the intake ports 10 communicate with the inflow passage 11 through the inside of the fixed base 1. Reference numeral 12 designates an outflow passageway projecting from the rotor guide frame 8 and facing this receiving groove 9.

To explain this effect now, first, this high-pressure gas is obtained using, for example, the gas pressure of the refrigerant in a refrigeration engine or the air pressure of a compressor.

Here, the high-pressure gas 8 is guided to inflow passages 11 arranged at 90° intervals on all sides on the left and right fixed bases 1.1, and the high-pressure gas inlet 10 at the tip of the inflow passage 11 is introduced into the casing. The water alternately flows into four crescent-shaped cylinder chambers 13 that are hermetically divided by the recess 2a of the cam surface 2, the side surface 3a of the rotor 3, and the inner surface 8a of the rotor guide frame 8. In this case, the left and right cylinder chambers 13, 13
．． 13. In '13, the concave and convex waves of the casing cam surfaces 2, 2 are placed in a symmetrical position (one side has a convex portion 2b and the other side has a concave portion 2a) and is located in the center.

That is, for the sake of explanation, first of all, starting from the fact that high-pressure gas A flows in from the intake port 10 of one fixed base 1, WIB Fig. 1
In the developed view, the gas pressure of the high-pressure gas A flowing in from the intake port 10 at the lower position on the left side (in the figure) presses the plate surface of the sliding blades 5 arranged orthogonally. Moving blade 5
The rotor 3 itself to which the rotor 3 is attached begins to rotate about the shaft 4 in the direction of the jet flow. As described above, when the rotor 3 rotates, the sliding blades 5 are in contact with the casing cam surfaces 2, 2, which are opposed to each other with a certain gap at both ends. ), and as a result, the cylinder chamber 13a, which was previously a small chamber, becomes a recessed portion 2a in which the cam changes position in the cylinder chamber 13.
The sliding blade 5 is gradually expanded in accordance with the increase in pressure (see Fig. 8), and the pressing area of the protruding sliding blade 5 is also enlarged, further increasing the pressing force. Of course,
This means that the two wJll1 blades in the front and rear positions are 5,5
Both operate in the same way.

In addition, the cylinder chamber 13b, which is in the forward position in the rotational direction of the sliding vane 5 (upper side in the drawing), is filled with low-pressure gas B, which has no suppressing effect. The low-pressure gas B is a cylinder chamber 13b that shrinks in inverse proportion to the cylinder chamber 13a that is expanded by the high-pressure gas 8.
Therefore, from the inside of the rotor 3 from the gas exhaust groove 6 provided on the front surface of the sliding blade 5 in the rotation degree direction, a ■-shaped The gas is guided to the annular gas guide groove 7, passes through the annular receiving groove 9 of the rotor guide frame 8 facing the annular gas guide groove 7, and is exhausted to the outflow passage 12.

On the other hand, the sliding vane 5 protruding toward the lower right side position in FIG. In this case, the cylinder chamber 13d in front of the sliding vane 5 is gradually reduced in size, so that the low-pressure gas B is exhausted from the gas exhaust groove 6 of the sliding vane 5 via the rotor 3. In this state, as the right end of the sliding blade 5 approaches the apex of the convex portion 2b, the pressing area further becomes smaller, and when the right end of the sliding blade 5 reaches the position e of the apex of the convex portion 2b, the high pressure in the cylinder chamber 13c The pressing area of the gas A becomes zero, and the pressing area of the sliding blade 5, which has slid to the opposite position (left side) at this time, becomes maximum (100%) and receives the gas pressure of the high-pressure gas A. After that, as the rotor 3 rotates, if the right end of the sliding blade 5 passes the apex e of the convex portion 2b, (
(See Figure 8 (■)), the high-pressure gas intake port 10 faces a position slightly past this apex 0, so the rear surface of the sliding blade 5 that protrudes slightly to the right from the rotor 3 position immediately becomes a pressing area. Thereafter, as the pressing area of the sliding vane 5 increases sequentially, the suppressing area on the opposite side (left side) decreases (in the developed diagram, the focal area is the high pressure gas area A, and the thin diagonal line area is the low pressure gas B area). area).

-8-1 In this way, the recesses 2a of the cylinder cam surfaces 2, 2 are formed on both sides with the rotor 3 disposed in the center as a boundary.

A crescent-shaped cylinder chamber 13a formed with 2a
, 13b, 13c, and 13d are arranged in a staggered arrangement with left and right alternating, and each chamber has a high-pressure gas intake port 10, so that the sliding blades 5, 5, which are slidable perpendicular to the 0-tar 3, have Either of the gas pressures is applied, and as a whole, both wings are substantially suppressed, thus making the rotation of the rotor 3 smooth.

Also, the low pressure gas B remaining on the front surface of the WIvJ blade 5 in the rotational direction is removed when the gas exhaust groove 6 of the sliding blade 5 is wide and at least at an intermediate position (a position where one of the tips does not reach the apex e of the convex portion 2b). ) and communicates with the left and right cylinder chambers 13, 13, flexibility is created in the exhaust action of the low-pressure gas B, and from this point of view as well, smooth exhaust can be achieved. Since this device is a compact disk-shaped device as a whole, it is also possible to obtain human driving force by connecting a plurality of devices as shown in FIG. 9, for example.

<Effects of the Invention> As described above, the rotary complete high-pressure gas rotating device of the present invention has two disc-shaped fixed bases with a casing cam surface and two sliding blades, and has a simplified rotor and rotor guide frame. Because of this structure, the entire device becomes compact. Moreover, the number of cylinder chambers divided by the sinusoidal casing cam surface, rotor, and sliding blades is small (four chambers are arranged alternately on the left and right, and the sliding blade returns to its original position by rotating 180 degrees, so Because it uses a double-blade drive system, it can rotate at high speed and efficiently convert gas pressure energy into rotational energy.Of course, this high-pressure gas
Refrigerant pressure.

It can be used with anything that obtains high-pressure gas such as air pressure, etc., and is highly versatile. Further, the high pressure gas supply of the present invention may be directly led to each cylinder chamber,
Unlike conventional pressurized engines, it does not require accessory parts such as distribution valves, and is a robust type that does not cause breakdowns or malfunctions. In addition, since the low-pressure gas is exhausted after use through the rotor from the sliding vane itself that slides in the cylinder chamber, it is possible to exhaust the gas without strain. It is also possible to connect a plurality of devices, and if necessary, the sinusoidal wave shape of the casing cam surface and the number of sliding blades can be increased or decreased.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention, and FIG. 1 is a partially cutaway slope view, FIG. 2 is a slope view with the circumference separated, and FIG. Il
, III is an explanatory diagram showing the sliding state of the sliding blades in the rotor, FIG. 4 1. T[ is a front view showing the inner surface of the fixed base part, FIG. 5 is a front view of the rotor, FIG. 6 is a front view of the rotor guide frame, and FIG. 7 is a front view of the rotor guide frame. I is an explanatory diagram showing the exhaust state of the sliding vanes, Figure 8 I, n, and fir are developed diagrams showing the relationship between the casing cam surface, rotor, and sliding vanes, and Figure 9 is a plane with multiple units connected in series. -01...Fixed base, 1a...Side surface, 2...Casing cam surface, 2a
... Concave portion, 2b... Convex portion, 3... Rotor, 4.
・・Shaft, 5・Sliding vane, 6・Gas exhaust groove, 7・
...Annular gas guide groove, 8...Rotor guide frame, 9.
...Annular receiving groove, 10...Intake port, 11...Inflow passage, 12...Outflow passage. Figure 6 (If) (I) Figure 9 Figure 8 (I) (II) (III)

Claims (1)

[Claims] 1. A pair of disk-shaped fixed bases with symmetrically formed casing cam surfaces with a sinusoidal cross section and uneven parts on opposing sides.
The opposed casing cam surfaces face each other with a constant gap, and a rotor having a width such that both side surfaces contact the convex portion of the gauging cam surface is mounted between the fixed bases, and each of the casing cam surfaces The four-part space is used as a cylinder chamber,
Further, a sliding blade having a length such that both ends thereof contact the opposing casing cam surface is mounted on the peripheral edge of the rotor in parallel with the axial direction, and a gas exhaust groove is provided on the front surface of the sliding blade in the rotational direction. An annular gas guide groove provided on the outer circumferential surface of the rotor is communicated, and the gas guide groove is guided to a discharge hole of a rotor guide frame that is located between both fixed bases and covers the rotor, and each convex on the casing cam surface of both fixed bases is connected. A rotary complete high-pressure gas rotating device characterized by having a high-pressure gas intake port facing the vicinity of the rotary unit.