JPS6157951B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a rotating piston positive displacement fluid device;
In particular, it relates to a fluid device that takes in atmospheric air and is used at an exhaust pressure in the range of 1.3 to 2 atmospheres, and is most suitable for, for example, a supercharger for an internal combustion engine.

Among conventional fluid devices, 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. There are two types of compressors: positive displacement compressors, whose main purpose is to obtain a large amount of pressure by trapping a certain amount of air in a cylinder and then discharging it against the pressure on the discharge side. Either type of compressor was used. Here, speed type compressors or blowers have the advantages and disadvantages of being able to obtain a high flow rate but not high pressure, and positive displacement compressors allowing high pressure but not a large flow rate.
In conventional air compressor or blower application products,
It was sufficient to use either the velocity type or the volumetric type. However, in recent years, superchargers, which greatly increase the output of existing internal combustion engines by supercharging the intake air, have been developed to take in atmospheric air and raise its temperature to an intermediate pressure of about 0.5 atmospheres, while still converting it into a flow rate. In recent years, there has been a demand for compressors or blowers with characteristics intermediate between those of the velocity type and the positive displacement type, which require a medium flow rate of about 5 to 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 when it is used in automobiles, agricultural machinery, construction machinery, etc., which are powered by the main shaft of the internal combustion engine. The equipment must be installed in such a way that it fits within the engine room of the existing machine and does not affect other functions. Traditionally, Saginaw-type or Roots-type fluidic devices have been used for such applications, but they are mostly applied to stationary devices and are not suitable for portable devices or automobiles due to their size and weight. It was hot. Particularly when mounted on a car, it is desirable to have a small shape in the lateral direction, although it may be somewhat long in the length direction.

In addition, in the case of a supercharger that obtains driving power from the main shaft of the engine using a power transmission device such as a gear or belt, the increase in engine output obtained by supercharging is equal to the power required to drive the supercharger. It is difficult to obtain a supercharger that pumps air with high volumetric efficiency over a wide rotation speed range and also has high total pressure efficiency, so it is difficult to obtain a supercharger with a high total pressure efficiency. It has the disadvantage of requiring large cost and space.

Furthermore, it is desirable for automotive supercharging equipment to be able to add a supercharging/non-supercharging switching device that can perform supercharging only when a supercharger is needed, but conventional mechanisms do not allow for switching from non-supercharging to supercharging. Since a large peak torque is required during switching, smooth switching cannot be performed.

A rotating cylindrical piston type positive displacement fluid device is one that can eliminate such defects and is particularly suitable for automobile superchargers. This rotating piston type fluid device has a cylindrical casing that constitutes a housing,
a fixed cylindrical member disposed in the center of the casing and having a cylindrical surface concentric with the inner wall surface of the casing;
A vertical partition plate arranged to extend in the axial direction between the casing and the fixed cylindrical member, and a vertical partition plate arranged in the annular space formed between the casing and the fixed cylindrical member to extend the partition plate in the radial direction. The rotating cylindrical member has a slot formed therethrough, a main shaft extending and supported in the center of the housing for driving the rotating cylindrical member, and a rotation prevention mechanism for preventing rotation of the rotating cylindrical member. One end of the partition plate is fixed to the fixed cylindrical member, and both ends are arranged with a gap between them and the inner wall surface of the front and rear ends of the housing so that the rotating cylindrical member does not interfere with the rotating cylindrical member at any crank angle. ing. Therefore, the suction side and the discharge side communicate with each other through this gap, and especially when a rotation prevention mechanism is provided between the inner wall surface of the casing and the end face of the rotating cylindrical member, this gap becomes large.
It had the defect that the volumetric efficiency decreased.

In addition, although it is advantageous to have a shape that is long in the axial direction and small in the lateral direction, especially when installed in a car, in the conventional technology, the shaft support of the swing piston is cantilevered, so the shaft When the directional dimension is increased, the rotating cylindrical member tends to bend due to compressive force and centrifugal force, making it difficult to support it accurately.

An object of the present invention is to provide a volumetrically efficient fluidic device that eliminates such defects.

Another object of the present invention is to provide a fluid device in which lubrication of a rotation prevention mechanism section can be performed separately from a fluid suction/discharge operation section.

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

That is, the present invention provides a housing comprising a cylindrical casing and a front housing disposed on one end surface of the casing, a fixed cylindrical member disposed in the center of the casing and having a cylindrical surface concentric with the inner wall surface of the casing; A vertical partition plate extends in the axial direction between the casing and the fixed cylindrical member, and a slot is provided in the annular space formed between the casing and the fixed cylindrical member and passes through the partition plate in the radial direction. and a rotating cylindrical member whose front and rear end openings are closed by closing plates, and a pair of eccentric crank parts are formed at the front and rear of the main shaft which extends in the center of the housing and is supported by bearings at the front and rear ends of the housing. At the same time, in the positive displacement fluid device in which the rotating cylindrical member is supported via a bearing on the eccentric crank portion, and fluid is sucked and discharged by rotating the rotating cylindrical member, the front end closing plate of the rotating cylindrical member is An annular protrusion extending axially forward from the pivoting cylindrical member support bearing formed in the center is formed on the end face of the closing plate, and extending radially outward from the end face of the protrusion so as to be substantially equal to the diameter of the pivoting cylindrical member. A rotation prevention mechanism for the rotating cylindrical member is formed between the end face of the flange portion and the inner wall surface of the front housing, and a rotation prevention mechanism is provided between the front end closing plate of the rotating cylindrical member and the flange portion. It is characterized by disposing an annular plate divided along the radial direction, thereby making it possible to reduce the gap between the fixing member facing the partition plate.

The basic structure of the present invention is that the main shaft of the rotating piston is supported on both sides at the front and rear ends of the housing, thereby reducing the deflection of the rotating cylindrical member due to compressive force and centrifugal force when the axial dimension is increased. It is possible to suppress it.

Further, by disposing a sealing member between the end face of the rotating cylindrical member and the fixed member, the space in which the rotation prevention mechanism is disposed and the space in which fluid suction and discharge operations are performed can be completely separated.

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. 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 provided at 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 core 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 inner side of the core cylindrical member 19 is a hollow portion 191, and support portions 192 and 193 extending radially inward are formed at the front and rear ends of the inner wall surface.
The core cylindrical member 19 is supported by arranging the bearings 92 and 193 on the bearings 20 and 21.
Note that the inner end of a partition plate 14 that separates the suction hole 15 and the discharge hole 16 is fixed to the core cylindrical member 19, so that the core 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.
3 and 24, the front and rear ends are closed plates 222, 22
A rotating cylindrical member 22 is closed by 3 and disposed so as to wrap around the core cylindrical member 19. As shown in FIG. 3, 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 at this time, a slot 221 extending in the axial direction is formed. ing. Furthermore, a bearing press-fit portion provided at the center of a closing plate 222 that closes the front end opening of the rotating cylindrical member 22 has a cylindrical protrusion 222 that protrudes forward in the axial direction.
A is formed at the end of the protrusion 222a, and the rotating cylindrical member 22 extends radially outward and has a diameter.
The flange portion 222b has a diameter that is substantially the same as that of the flange portion 222b.
has been established. Therefore, a gap 25 is formed between the flange portion 222b and the closing plate 222, and an annular plate 26 divided along the radial direction is disposed in the gap 25, as shown in FIG. . Here, the annular plate 26 is held and fixed between the front housing 12 and the cylindrical casing 11.

Flange portion 222b and front housing 12
A suitable rotation prevention mechanism 27 is disposed between the rotary cylindrical member 22 and the inner wall surface thereof to prevent rotational movement of the rotating cylindrical member 22. In this embodiment, the rotation prevention mechanism 27 uses a crank type coupling mechanism as shown in FIGS. 2 and 4. In the case of this mechanism, as shown in FIG.
Rotation operation is prevented by sandwiching the ring between the ring and the annular recess 273 formed in the ring. In addition, both recesses 2
A Teflon sleeve 28 or a bearing is fitted between 72, 273 and the crank 271.

Furthermore, a balance weight 29 is fitted in the cavity 191 of the core cylindrical member 19 on the main shaft 13 so that a perfect dynamic balance can be maintained when the rotating cylindrical member 22 and the like perform circular orbital motion. The center of gravity is the eccentric crank part 131, 132
It is located in the direction 180° opposite to the angle of.

The fluid sucking and discharging operation of this device will be described below with reference to FIGS. 5a to 5h.

5a to 5h, 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. 5a to 5b, 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. 5c to 5f, 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 core 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. 5d to 5f), sealing is achieved from the suction side at point _Q1 , and fluid discharge begins. As is clear from Figures 5g to 5c, the volume of this space B is:
It decreases as the rotating cylindrical member 22 moves, and the fluid continues to be discharged, while new fluid intake begins on the opposite side via the contact point Q.

In the fluid intake/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 side of the core cylindrical member 19 A gap is created between the wall surface and the suction hole 15 and the discharge hole 16 when considered quasi-statically. 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 be a big 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 suction 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. Further, the length of the partition plate 14 is the same as the length of the core cylindrical member 19, and the length of the rotating cylindrical member 22 is the same as that of the core cylindrical member 19.
In principle, it is not possible to make the length the same as that of the rear end surface of the partition plate 14 and the closed end 11 of the casing 11.
2 inner wall surfaces and between the front end surface of the partition plate 14 and the annular plate 2
A gap will be created between the end face of 6 and this will also allow communication between the suction and exhaust holes,
Even under such conditions, the performance at high speed rotation is satisfactory for the reasons mentioned above.

FIG. 6 is a partial sectional view of a fluid device showing another embodiment of the present invention. In this embodiment, a groove 30 is formed on the outer peripheral end surface of the closing plate 222 of the rotating cylindrical member 22, and a sealing member is inserted into the groove 30. 31, and the closing plate 222
The configuration is such that a seal is formed between the end face of the annular plate 26 and the annular plate 26. This makes it possible to completely separate the space in which the rotation prevention mechanism 27 is disposed and the space in which fluid is sucked and discharged. In this embodiment, an O-ring 32 is disposed within the groove 30 to press the seal member 31 in the axial direction.

As described above, the present invention forms a cylindrical protrusion that protrudes axially forward along the bearing press-fit portion in the center of the closing plate that closes the front end opening of the rotating cylindrical member,
A flange portion extending radially outward is provided at the end of the protrusion, a rotation prevention mechanism is provided between the flange portion and the inner wall surface of the front housing, and an annular plate is provided in the gap between the flange portion and the closing plate. Even if the rotation prevention mechanism is provided at one end of the rotating cylindrical member, it is possible to reduce the gap between the end of the partition plate and the fixed member.
Decrease in volumetric efficiency due to this gap can be prevented.

In addition, since a sealing member is provided between the flange portion and the end face of the rotating cylindrical member, the space in which the rotation prevention mechanism is installed and the space in which the fluid suction/discharge operation is performed can be completely separated. Since grease can be filled in the provided space, the movable parts can be well lubricated.

[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,
Fig. 3 is a perspective view of the rotating cylindrical member, Fig. 4 is a perspective view of a crank constituting the rotation prevention mechanism, Fig. 5 is a diagram for explaining the operation of the fluid device according to the present invention, and a to h are cranks, respectively. 6A is a sectional view showing another embodiment of the present invention, and FIG. 6B is an enlarged sectional view of section A in FIG. 6A. 11... Cylindrical casing, 12... Front housing, 13... Main shaft, 131, 132...
Eccentric crank portion, 14... Partition plate, 19... Core cylindrical member, 22... Swivel cylindrical member, 221... Slit, 222, 223... Closing plate, 222a...
...Cylindrical protrusion, 222b...Flange part, 26...
Annular plate, 27... Rotation prevention mechanism, 31... Seal member.

Claims (1)

[Scope of Claims] 1. A housing consisting of a cylindrical casing and a front housing disposed on one end surface of the casing, and a fixed cylindrical member disposed in the center of the casing and having a cylindrical surface concentric with the inner wall surface of the casing. A rectangular hole extending in the axial direction between the casing and the fixed cylindrical member and provided on the side surface of the casing is divided into two, one being an intake hole and the other being an exhaust hole. A partition plate is fixed to the fixed cylindrical member, and a slot is formed in the annular space formed between the casing and the fixed cylindrical member to pass through the partition plate in the radial direction, and the front and rear end openings are closed by closing plates. a closed rotating cylindrical member, a pair of eccentric crank parts are formed at the front and rear of a main shaft extending in the center of the housing and supported by bearings at the front and rear ends of the housing; In a positive displacement fluid device in which the rotating cylindrical member is supported via a bearing and sucking and discharging fluid by rotating the rotating cylindrical member, the rotating cylindrical member is formed at the center of a front end closing plate of the rotating cylindrical member. A flange having an annular projection extending axially forward from the support bearing portion on the end surface of the closing plate, extending radially outward from the end surface of the projection and having a diameter substantially the same as the diameter of the pivoting cylindrical member. A rotation prevention mechanism for the rotating cylindrical member is provided between the end face of the flange part and the inner wall surface of the front housing, and a circle divided into two diametrically is provided between the front end closing plate of the rotating cylindrical member and the flange part. A rotating cylindrical piston type positive displacement fluid device characterized by having an annular plate arranged therein. 2. The rotating cylindrical piston type positive displacement fluid device according to claim 1, wherein the outer peripheral portion of the annular plate is sandwiched and fixed between a front housing and a cylindrical casing. 3. The rotating cylindrical piston-type volume according to claim 1 or 2, characterized in that a sealing member is disposed between the front end closing surface of the rotating cylindrical member and the end surface of the annular plate. type fluid device.