JPS6157953B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotating piston type positive displacement fluid device, and particularly to a fluid device that takes in atmospheric air and is used with an exhaust pressure in the range of 1.3 to 2 atmospheres, such as a supercharger of an internal combustion engine. It is the most suitable for

Conventional fluid devices used as air compressors include speed type compressors, which aim to increase air flow by rotating fan blades at relatively high rotational speeds, and piston type or rotary vane type compressors. It can be divided into positive displacement compressors, which mainly aim to obtain large pressure by trapping a certain amount of air in a cylinder and discharging it against the discharge side pressure. , either type of compressor was used depending on the purpose. Here, speed type compressors or blowers have the advantages and disadvantages of being able to obtain a large flow rate but not high pressure, and positive displacement compressors have the advantages and disadvantages of obtaining high pressure but not large flow rates. For air compressor or blower application products, it has been sufficient to use either the velocity type or the positive displacement type. However, in recent years, the output of existing internal combustion engines has been greatly increased by supercharging the intake air.
Although the pressure is increased to about 0.5 atm, the flow rate is 5
There is a growing demand for compressors or blowers that have characteristics intermediate between velocity type and positive displacement type, which require a medium flow rate of about 10 m ³ /min.

In the case of a supercharger, if its size and weight are too large compared to the internal combustion engine itself, there is no benefit, especially in cars, agricultural machinery, construction machinery, etc., which are powered by more power than the main shaft of the internal combustion engine. In this case, it must be installed in such a way that it fits within the engine room of the existing machine and does not affect other functions. Particularly when mounted on a car, it is preferable to have a small diameter, although it may be somewhat long in the length direction.

A rotating cylindrical piston type positive displacement fluid device is used for such applications, but if the diameter of the device is made smaller and the length is increased instead, as in the case of using it as an automobile supercharger, it will inevitably cause problems. The length of the pivoting piston is also large compared to its diameter. However, in the past, when the swing piston was driven via the crank mechanism of the main shaft, the rotation of the swing piston was prevented by a rotation prevention mechanism placed between the inner wall of one end of the casing and the end face of the swing piston. The piston had the defect of twisting and vibration or noise during high-speed movement.

An object of the present invention is to provide a fluid device that does not generate vibrations or sounds even during high-speed motion.

Another object of the invention is to achieve the above objects with a simple construction.

That is, the present invention provides a housing having a cylindrical casing with one end closed, a front housing disposed at the other end of the casing, and a cylindrical casing disposed in the center of the housing and concentric with the inner wall surface of the casing. a fixed cylindrical member having a surface, a vertical partition plate extending in the axial direction between the casing and the fixed cylindrical member, and a vertical partition plate disposed within an annular space formed between the casing and the fixed cylindrical member, a rotating cylindrical member whose front and rear ends are closed and has a slot for penetrating the main shaft in the direction of the main shaft; and a pair of eccentric crank parts formed at positions apart from each other on the main shaft within the housing to support both ends of the rotating cylindrical member, and the eccentric crank parts are rotated by rotation of the main shaft. In a positive displacement fluid device that sucks and discharges fluid by rotating a rotating cylindrical member, a rotation prevention mechanism for preventing rotational movement of the rotating cylindrical member is installed between the inner wall surface of the front housing and the front end surface of the rotating cylindrical member. It is characterized in that it is disposed between the inner wall surface of the housing and the rear end surface of the swivel cylindrical member, and it is possible to prevent the swivel cylindrical member from twisting even during high-speed rotation.

The present invention will be described below with reference to drawings showing embodiments.

FIG. 1 is a perspective view of a positive displacement fluid device showing an embodiment of the present invention, and the fluid device 1 has a cylindrical casing 11 with one end open and the other end closed, and the open end of the casing 11 is closed. front housing 12
It has a housing 10 consisting of. Note that a protrusion 111 forming a rectangular opening extending from near the front end to near the rear end is formed on the outer wall surface of the casing 11, and a partition plate 14 extending in the axial direction is formed in the center of the opening.
is provided to divide the opening into two, an intake hole 15 and a discharge hole 16. Further, a main shaft 13 passes through the center of the front housing 12.

Here, the configuration will be explained with reference to FIG. 2, which is a longitudinal cross-sectional view of the fluid device 1 shown in FIG. The front housing 12 is rotatably supported by ball bearings 17 and 18 press-fitted into a main shaft through hole 121 formed in the center of the front housing 12, respectively. A fixed cylindrical member 19 having an outer wall surface concentric with the inner wall surface of the casing 11 is disposed on the outer periphery of the main shaft 13 via two bearings 20 and 21. That is, the inside of the fixed cylindrical member 19 is a hollow part 191, and support parts 192 and 193 extending radially inward are formed at the front and rear ends of the inner wall surface.
The fixed cylindrical member 19 is supported by arranging the bearings 92 and 193 on the bearings 20 and 21.
Note that, as shown in FIG. 3, the inner end of a partition plate 14 that separates the suction hole 15 and the discharge hole 16 is fixed to the fixed cylindrical member 19, so that the fixed cylindrical member 19 is stationary and fixed. .

Eccentric crank parts 131 and 132 provided at the same angular position are formed at the front and rear ends of the main shaft 13, and bearings 2 are mounted on the eccentric crank parts 131 and 132.
A rotating cylindrical member 22 is provided which is closed at both front and rear ends via 3 and 24 and is disposed so as to wrap around the fixed cylindrical member 19. The rotating cylindrical member 22 moves in a circular orbit due to the rotational movement of the eccentric crank parts 131 and 132, but in order to avoid interference with the partition plate 14, a slot 221 extending in the axial direction is provided as shown in FIG. is forming. In addition, the front end surface of the rotating cylindrical member 22 and the front housing 12
Appropriate rotation prevention mechanisms 25A and 25B are arranged between the inner wall surfaces and between the rear end surface of the rotating cylindrical member 22 and the inner wall surface of the closed end wall 112 of the casing 11 in order to prevent rotational movement of the rotating cylindrical member 22. has been done. Here, in this example, this rotation prevention mechanism 25
uses a ball coupling mechanism as shown in FIGS. 2 and 5. Ball coupling mechanism 2
The configuration of 5 is the same in both the front and rear, and the rotating cylindrical member 2
A hole 251a (FIG. 4 shows an example in which four holes are provided) is disposed on the end face of the steel ball 256 and has a diameter set so that the required turning radius can be obtained in combination with the steel ball 256. ) with a swivel ring 25
1. A swing race 252 fixed simultaneously to the swing ring 251 on both end faces of the swing cylindrical member 22 by pins to provide a transfer surface for the steel balls 256, and an annular recess formed in the inner wall face of the front housing 12 or the closed end wall 112. 12a, 112a and a fixed ring 254 having a hole 254a similar to that of the swivel ring 251, and an annular recess 12a, 112 in the front housing 12 or the closed end wall 112.
A fixing race 255 is fixed at the same time as the fixing ring 254 at the bottom of the frame by a pin (not shown) and provides a transfer surface for the steel ball 256, and a sandwiching support is provided between the hole 251a of the swivel ring 251 and the hole 254a of the fixing ring 254. The steel ball 256 is made of steel.

Further, the hollow portion 1 of the fixed cylindrical member 19 is located on the main shaft 13.
Within 91, a balance weight 26 is fixed by a key 27 so that a perfect dynamic balance can be maintained when the rotating cylindrical member 22 and the like perform circular orbital motion. It is 180 degrees opposite to the angle of 132. Note that the rotating cylindrical member 22 has a slot 2.
21 is formed, a notch may be provided in a part of the pivot ring 251 so that the center of gravity of the pivot ring 251 coincides with the central axis.

In the embodiment shown in FIG. 2, among the bearing support parts provided on the fixed cylindrical member 19, the rear end side support part 193 is formed integrally with the fixed cylindrical member 19, but the front end side support part 193 is formed integrally with the fixed cylindrical member 19. The support portion 192 is formed separately from the core cylindrical member 19 and is press-fitted into the inner surface of the fixed cylindrical member 19. Further, the front end side closing plate 222 of the rotating cylindrical member 22 is formed separately from the rotating cylindrical member 22 so that the fixed cylindrical member 19 can be inserted therein, and is fixed by caulking or the like during the assembly process. Furthermore, among the eccentric crank parts provided on the main shaft 13, the eccentric crank part 13 on the front end side
1 is formed separately from the main shaft 13 and is fixed with a key 28 during the assembly process.

The fluid sucking and discharging operation of this device will be described below with reference to FIGS. 6a to 6h.

6a to 6h, the crank angle of the main shaft 13 is 0°, α°, 90°, 180°-α°, 180°, 180°.
The positions of the pivoting cylindrical member 22 at degrees +α°, 270° and 360°−α° are shown. Here, 2α° is the opening angle of the slot 221 provided in the rotating cylindrical member 22.

As is clear from FIGS. 6a to 6b, in the process of turning the rotating cylindrical member 22 by α°, a point P ₁ is formed between the outer wall surface of one end of the rotating cylindrical member 22 and the inner wall surface of the casing 11. A sealed space A is formed and a gap is created between the outer wall surface of the other end of the rotating cylindrical member 22 and the inner wall surface of the casing 11, so that the fluid in the space A is discharged through this gap. As can be seen by following the sequence of FIGS. 6c to 6f, the discharge continues as the rotating cylindrical member 22 moves. The volume of the space A decreases with the movement of the rotating cylindrical member 22, and new fluid intake starts on the opposite side via the contact point P. As the fluid in this space A is discharged, the volume of the space B formed between the outer wall surface of the fixed cylindrical member 19 and the inner wall surface of the rotating cylindrical member 22 expands and takes in the fluid, thereby increasing the crank angle.
Between 180°-α° and 180°+α° (FIGS. 6d to 6f), sealing is achieved from the suction side at point _Q1 , and fluid discharge begins. As is clear from FIGS. 6g to 6c, the volume of this space B decreases with the movement of the rotating cylindrical member 22, and the fluid continues to be discharged from the opposite side via the contact point Q. , new fluid uptake begins.

In the fluid suction and discharge cycle as described above, when the crank angle is between -α° and +α°, the rotating cylindrical member 2
A gap is created between the outer wall surface of the rotating cylindrical member 22 and the inner wall surface of the casing 11, and when the crank angle is between 180°-α° and 180°+α, the inner wall surface of the rotating cylindrical member 22 and the outer wall surface of the fixed cylindrical member 19 are separated. A gap is created between them, and if considered quasi-statically, the suction hole 15 and the discharge hole 16 will communicate with each other due to the creation of the gap. However, if the opening angle 2.alpha..degree. of the slot 221 formed in the rotating cylindrical member 22 is designed to be minimized, this gap will not pose a major problem if the device has a pressure ratio of 1 to 2. In particular, since this device uses a rotating cylindrical member with a relatively small radius, the moment of inertia of the moving part is smaller than that of a rotary type device in which the piston part rotates, and the two cylindrical surfaces with similar curvatures are very close together. The intake and exhaust pressures are separated by being close to each other, and the movement of air due to the rotation of the main shaft does not involve shearing the air like in vane rotary devices, so high speed rotation can be performed without consuming large horsepower. The time that the suction and exhaust holes communicate can be shortened, and there is no major loss. In addition, the length of the partition plate 14 is the same as the length of the fixed cylindrical member 19, and cannot be made the same as the length of the rotating cylindrical member 22 in principle. A gap will be created between the inner wall surfaces of the closed end 112 of 11, and this will also allow communication between the suction and exhaust holes, but even in this state, the performance at high speed rotation can be satisfied for the above-mentioned reasons. becomes.

As described above, in the present invention, rotation prevention mechanisms are provided between both closed ends of the swivel cylindrical member, the casing closed end wall, and the inner wall surface of the front housing, so that the swivel cylindrical member remains stable even during high-speed rotation. Rotational movement of the rotating cylindrical member can be prevented at both ends,
Therefore, even if the axial length of the swiveling cylindrical member is long, the swiveling cylindrical member can be prevented from twisting during high-speed rotational driving. Therefore, it is possible to prevent vibration of the device or generation of internal noise caused by twisting of the rotating cylindrical member.

Furthermore, when a ball coupling mechanism is used as the rotation prevention mechanism, it becomes possible to prevent the rotation of the rotating cylindrical member with a simple configuration.

[Brief explanation of the drawing]

FIG. 1 is a perspective view of a fluid device showing an embodiment of the present invention, FIG. 2 is a sectional view of the fluid device shown in FIG. 1,
3 is a cross-sectional view of FIG. 2, FIG. 4 is a perspective view of the rotating cylindrical member, FIG. 5 is a cross-sectional view of FIG. In the diagrams a to h, the positions a to h respectively show states at different positional relationships of the crank angles. 11... Cylindrical casing, 12... Front housing, 13... Main shaft, 131, 132...
Eccentric crank portion, 14... Partition plate, 19... Fixed cylindrical member, 22... Swivel cylindrical member, 221... Slot, 25... Rotation prevention mechanism.

Claims (1)

[Claims] 1. A housing having a cylindrical casing with one end closed, a front housing disposed at the other end of the casing, and a front housing disposed at the center of the housing and concentric with the inner wall surface of the casing. A fixed cylindrical member having a cylindrical surface, a vertical partition plate extending in the axial direction between the casing and the fixed cylindrical member, and a partition plate arranged in an annular space formed between the casing and the fixed cylindrical member. a rotating cylindrical member whose front and rear ends are closed and which has a slot extending through the housing in the radial direction, and extends in the center of the housing;
a main shaft whose front and rear ends are supported by bearings between the closed end of the casing and the front housing; and a pair of main shafts formed at positions apart from each other on the main shaft within the housing to support both ends of the rotating cylindrical member. In a positive displacement fluid device having an eccentric crank section, the rotational movement of the rotating cylindrical member performs a fluid suction/discharge operation by rotating the rotating cylindrical member via the eccentric crank section by rotation of the main shaft. A rotating cylindrical piston type volume, characterized in that a rotation prevention mechanism for preventing rotation is disposed between the front housing inner wall surface and the front end surface of the rotating cylindrical member, and between the housing inner wall surface and the rear end surface of the rotating cylindrical member. formula fluid device. 2. The rotation prevention mechanism is fixed to a rotating ring having a plurality of holes fixed to the front end surface and rear end surface of the rotating cylindrical member, and a fixing member having a plurality of holes fixed to the inner wall surface of the front housing and the inner wall surface of the closed end of the casing. The rotating cylinder according to claim 1, characterized in that it is a ball coupling mechanism comprising a ring and a steel ball sandwiched between a hole in the rotating ring and a hole in the fixed ring that face each other. Piston type fluid compressor.