JPS60187783A - Vane type suction and compression device for fluid - Google Patents

Abstract

PURPOSE:To reduce abrasion and breakage of casing and vane and improve the operating efficiency of the device by a method wherein the casing, accommodating a rotor equipped with vanes, is made rotatable and relative speed between the rotation of rotor and the rotation of the casing is reduced. CONSTITUTION:When the rotor 4 is rotated in a high-speed by the high-speed rotation of a driving shaft 3, the vanes 6 slide in vane accommodating grooves 9 and are projected out of the outer circumference of the rotor 4 while the tip ends of the vanes 6 contact with the inner peripheral wall of the casing 5 and push the same strongly by a centrifugal force. Then, the torque of the rotor is transmitted to the casing 5 through the vanes 6 and the casing 5 is also rotated together with the rotation of the rotor 4. The relative speed between the rotation of the casing 5 and the rotation of the rotor 4 is very small, therefore, immoderate force will never be applied to the reverse direction of the rotation of the vanes, abrasion and breakage of the tip ends of vanes 6 as well as the casing 5 may be reduced and the operating efficiency of the device may be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides fluid suction that reduces wear and damage to the vanes and the housing and increases operating efficiency by rotating the vanes inside a rotatably supported housing. This relates to compression wires.

In a conventional vane-type suction compressor, a casing that houses a rotor that surrounds the vanes is fixed in a non-rotatable manner. Therefore, when the rotor is rotated, the centrifugal force causes the vanes to protrude from the circumference (111) of the rotor toward the inner wall of the casing, and as the rotor rotates, the tips of the vanes will rub against the inner wall of the casing. If the tips of the vanes or certain inner walls of the housing are worn out, or if the vanes bend in the opposite direction to the rotational direction when the rotor rotates, the outer peripheral surface of the rotor or two adjacent vanes may become damaged. The airtightness of the space formed by the inner wall of the casing is degraded, and as a result, the compression efficiency of the vane-type suction compressor is significantly reduced.In addition, when the rotor rotates, centrifugal force Rotational force is applied to the vane that presses the tip against the inner wall of the casing, so
Sometimes the vanes can break.

This invention was made based on the above-mentioned circumstances, and aims to provide a vane-type suction compressor that reduces wear and damage of the housing and vanes and improves operating efficiency.

To achieve the above object, the present invention provides a vane-type suction compressor in which a housing housing a rotor provided with vanes is made rotatable, and the relative speed between the rotation of the rotor and the rotation of the V body is reduced. It is characterized by the fact that

Next, an embodiment in which the present invention is used as a combination type will be described with reference to the drawings.

FIG. 1 is a longitudinal cross-sectional view showing a vane-type suction and compression device, which is an embodiment of Jin's invention, and FIG.
It is an A-line sectional view.

As shown in FIGS. 1 and 2, the vane-type suction and compression device 1 includes a pair of support parts, a drive shaft 3, and a rotary tag 1.
Includes a housing S and a vane 4.

A pair of supporting members J, which are arranged opposite to each other with a constant distance Df,! Each has a push-through hole 7 into which the drive shaft 3 is inserted. The drive shaft 3 is inserted from the push-through hole 7 of one support member Y to the insertion hole 7 of the other support member Y, and the center line O8 of this drive shaft 3 and the center line 0 of this insertion hole 7. The drive shaft 3 is connected to the pair of support portions so that they are different from each other.

Support it so that it can rotate freely.

Between the pair of support parts @ko1.2, there is a center aO1 of the drive shaft 3.
A cylindrical rotor q having a center line 01 that coincides with the rotor q is rearranged, a drive shaft 3 is inserted into the center of this rotor tag, and the rotor q is
and the drive shaft 3 are integrally coupled.

Furthermore, a housing S is disposed between the pair of support members, and this housing 5 has a cylindrical inner chamber g having an inner side surface that airtightly contacts both end surfaces of the rotary tag. Store the low tag in the inside g so that the center line 01 of the low tag and the center line 03 of the inner chamber rim do not match, and the center line Os of the inner chamber g and the center line O7 of the push-through hole 7 match. And, it is rotatably supported by the pair of support members 2.

On the outer peripheral surface of the low tag, there is a center line O8 of the low tag.
A plurality of vane storage grooves 9 are provided at equal intervals, each having a predetermined depth toward , a length extending through the low tag from one end surface to the other end surface, parallel to the center M O+, and a predetermined width. In this embodiment, six vane storage grooves are connected to adjacent vane storage grooves. , q are set at equal intervals so that the central angle θ formed by q is 60°. A vane 6 having an end surface that can be temporarily attached to the inner circumferential surface and inner side surface of the inner chamber is slidably inserted into each vane storage groove 9.

On the outer circumferential surface of the rotor q between adjacent vanes 6, 6, there is a second suction passage /l that communicates with the first suction passage 10 opened in the drive shaft 3 and the outer circumferential surface of the rotor tag. A one-way valve is provided at the opening in the surface, which allows only the fluid flow i from the second suction path l/ into the space between the outer circumferential surface of the Rotag and the inner circumferential wall surface of the housing S, but prevents the fluid from flowing back in the opposite direction. , for example, a first Chutsky pulp/co is provided. Additionally, on the outer circumferential surface of the rotor tag between the adjacent through vanes 6.6, in addition to this first Chucky valve saw, there is also a first discharge passage /3 opened in the drive shaft 3 which communicates with the outer circumferential surface of the rotor t. The opening of the second discharge path /q on the outer peripheral surface of the rotor q only allows fluid to flow into the second discharge path /l from within the space between the outer peripheral surface of the rotor tag and the inner peripheral wall surface of the casing S. A one-way valve, for example a second Chucky valve is, is provided to prevent backflow of fluid in the opposite direction. The second Chucky valve/S is designed to open when a preset cranking pressure is exceeded.

The first suction passage 10 and the first discharge passage/3 are opened to face each other within the drive shaft 3.
The first suction passage 10 (1111) is connected to a fluid supply, such as an air cleaner (not shown), via a rotary joint (not shown) at the end of the first suction passage 10 (1111). A rotary joint (not shown) provided at the end of the drive shaft 3 on the first discharge path/3 side is connected to an appropriate @ phase requiring compressed gas, e.g. ).

As shown in FIG. 2, in the cross section of the rotor l (parallel to one end surface), the second suction passage // and the second discharge passage /l straddle the first suction passage 70 and the first discharge passage /3. radially extending from the center toward the outer peripheral surface of the rotary.

In addition, the drive shaft 3 is connected to a power source via a suitable power transmission means such as a pulley, a belt, a pinion, etc. Also,
In FIGS. 1 and 2, 1 indicated by /7 is a bearing device.

Next, the operation of the above configuration will be explained. The first discharge passage /3 and the second discharge passage /+ are filled with compressed gas as a result of the operation of this vane-type suction compressor, and this compressed gas flows through the second Chucky valve. /S to prevent leakage into the space between the outer circumferential surface of the low tag and the inner circumferential wall surface of the housing S.

Therefore, the drive shaft 3 is rotated at high speed by a power source (not shown), and the first suction passage 10 and the second suction passage // are communicated with the outside air.

When the rotor V rotates at high speed due to the high speed rotation of the drive shaft 3, the vane 6, which had been housed in the vane storage groove 9 until then, slides inside the vane storage groove 9 due to the centrifugal force, and the rotor q
The tip of the vane B contacts the inner circumferential wall on the left side of the housing, and the tip of the vane 74 strongly presses the inner circumferential wall of the housing S due to centrifugal force. Then, the rotational force of the rotor 1 is transmitted to the casing S via the vane 6, and the casing S also rotates along a hidden line along with the rotation of the rotor 1.

On the other hand, when each of the six vanes 6 protrudes to the inner circumferential wall surface of the housing S due to centrifugal force and presses it strongly, the two adjacent vanes A, B and the outer circumferential surface of the rotor q The inner circumferential wall surface of the housing S and the opposing inner side (lli surface)
As shown in Figure 2, to the six compression chambers A, /6B, 7c
c, /61), ibE, ibE are formed. 6
Compression chambers #A, /4B, #C, /Op', #E.

Focusing on the compression chamber A with the largest product among 74F, the compression chamber // and A are filled with the gas sucked in from the second suction passage // through the first Chatsky valve /2. There is. The rotation of the rotary and the casing S reduces the volume of the compression chamber/4A, so that the gas inside is compressed to the volume of the compression chamber 74B. Next, by further rotation of the rotor I and the casing S, the gas compressed into the volume of the compression chamber 76B is compressed into the volume of the compression chamber/compression chamber. In this way, the gas in the compression chamber 16A is compressed to the volume of the compression chamber //, C because the housing S also rotates via the vane 6 as the rotor l rotates, and the outer circumferential surface of the rotor l rotates. porcelain S
This is because the inner circumferential wall surfaces of the two are brought closer together and the volume is reduced. Also, the rotational speed of the rotary and the rotational speed of the left side of the casing are different, but compared to the rotational speed of the rotor when the casing cannot rotate like in the past, the relative rotational speed of the rotary with respect to the rotating casing. is much smaller, so no force is applied to the vane 6 in the opposite direction of rotation, and wear on the tip of the vane A is significantly reduced. No gas leaks between the

Further, a suppressing force of different strength acts on the inner circumferential wall surface of the casing S depending on the protruding state of the vane B, but since the walls mj that receive a strong pressing force move sequentially due to the rotation of the casing S,
Less likely to cause uneven wear on the inner peripheral wall surface.

The pressure of the gas when it is compressed from the compression chamber //, A to the volume of the compression chamber /6C is greater than the pressure of the gas in the second suction passage //, and the gas pressure in the second discharge passage /'7 is When the gas in the compression chamber/6A is compressed to the volume of the compression chamber/6C, this gas flows through the first Chatsky valve L- and the second Chatsky valve L-. There is no leakage from 1k.

When the gas is compressed to the maximum during the transition from the compression chamber/AC to the compression chamber/4D with the rotation of the rotary and the housing S and exceeds the cracking pressure, the second Chutsky valve/,
Since the opening opens, the compressed air in the compression chamber/AD leaks into the second exhaust path lq.

Furthermore, by the rotation of the rotor tag and the P body S, the rotor q
The inner circumferential wall surface of the housing S separates from the outer circumferential surface of the H-shrinking/A
The volume is increased from D to compression chamber 76F. Then, the valve pressure increases in the compression chambers /61) to /4F, so the first
Gas is drawn into the compression chambers /4D to //, F from the second suction passage // through the Chucky valve 12.

The compression chamber/
When the customer volume of 4F becomes that of compression chamber/4A, the above-mentioned process is repeated and the gas is compressed 1-J.

The embodiments in which the present invention is used as an air compressor have been described in detail above, but the present invention is not limited to the embodiments described above, and may be implemented with appropriate modifications within the scope of the gist of the present invention. It's hard to say what you can do.

In the embodiment, the center line 01 of the rotor q and the center i of the flute body S are aligned so that the outer circumferential surface of the rotor l is inscribed in the inner circumferential wall surface of the housing S. Although the relationship with l' U8 is determined,
The diameter line and rotor l tracing the center line 01 and the center 1iIOs
Outside Ii! The intersection with the d-curve is close to the inner peripheral wall on the left side of the housing,
The outer circumferential surface of the rotary and the inner circumference kj of the housing S that do not meet this point of intersection
center 1II so that there is a slight gap between it and the P plane.
The relationship between O+ and the center line 03 may be determined.

Further, the present invention is not limited to being used as a gas compressor as in the above embodiments, but can also be used as a liquid pump or a vacuum pump. When used as a coastal pump for water, oil, etc., the first suction path 10
It is sufficient to connect the first suction path IO to a liquid tank extension, and when used as an empty pump, it is not necessary to connect the first suction path IO to a vacuum passenger device or the like. In this case, the set pressure of the second Chucky valve IS may be set lower than that when used as a gas compressor so that it can be opened easily due to an increase in the internal pressure of the compression chamber/6.

In the embodiments described above, the first. 2nd Chatsky
Valve/2. /A; is provided at the opening on the outer peripheral surface of the low tag, but the first Chucky valve l- may be provided in the middle of the suction passage /l, and the second Chucky valve 1g may be provided in the middle of the discharge passage /ge. . In addition, the above embodiment has a second Chucky valve/
Although a predetermined pressure is set for S, a check valve may be provided in the second discharge path /1, and a relief valve may be provided in the first discharge path /3.

As detailed above, according to the present invention, the casing that houses the rotor also rotates with the rotation of the rotor, so that no excessive force is applied to the vanes that press against the inner wall surface of the casing during rotation. , it is possible to reduce wear on the tip surface of the vane and the inner circumferential wall surface of the housing, and it is possible to significantly improve the operating efficiency of the vane type suction and compression device.

[Brief explanation of drawings]

FIG. 1 is a gauze sectional view showing a vane-type suction and compression device which is an embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line A-A in FIG.
This is a sectional view taken along the line. L... Vane type suction compression device, Y... Support member, 3
... Drive shaft, S... Rotor, S... Housing, 4...
・Vane, g...inner chamber, w...vane storage groove, 10
...First suction path, l/...Second suction path, /ko...
1st Chucky valve, /3... 1st discharge path, ltI
...Second discharge path, lS...Second chat key palf,
/4A~74F...Compression chamber. Patent applicant: Toyo Densan Co., Ltd.

Claims (1)

[Claims] Identify a rotor having the same center line as that of a drive shaft that is rotatably supported by a support member, store the rotor, and contact one end of the rotor in an airtight manner.
l (A housing having a cylindrical inner chamber that shoulders the tl++ surface and having a center line different from the center line of the rotor is rotatably supported by the support member, and a vane storage groove is provided on the outer peripheral surface of the rotor. radially opening a plurality of holes, and slidably fitting vanes into these vane storage grooves, and openings of intake passages and discharge passages provided from the drive shaft to the rotor, respectively, on the outer circumferential surface of the rotor; The suction path is provided with a first one-way valve that only allows fluid to flow into the inner chamber of the casing, and the discharge path is provided with a first one-way valve that allows fluid to flow only into the inner chamber of the casing. A second one-way valve that only allows fluid to flow out is provided, and the volume of the compression chamber formed by the outer circumferential surface of the rotor, the adjacent vanes, and the inner wall of the casing is sequentially increased or decreased as the rotor rotates. A fluid vane-type suction and compression device, characterized in that the fluid sucked into a compression chamber from a suction path is compressed and discharged to a discharge path.