JPS6157952B2 - - 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 the air flow rate by rotating a fan plate at a relatively high rotation speed, and piston type or rotary vane type. 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. Depending on the type of compressor used. Here, velocity 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, which can obtain high pressure but not large flow rates. For air compressor or blower application products, it was sufficient to use either the velocity type or the positive displacement 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 increase the pressure to an intermediate pressure of about 0.5 atmospheres, while still reducing the flow rate. Compressors or blowers having 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/min, have come to be required.

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 shape that is somewhat long in the length direction but small in the lateral 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 a 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, and in order to obtain a small net power improvement. It has the drawback 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 switching from non-supercharging to supercharging. Since a large peak torque is required at the time of switching, smooth switching cannot be performed.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a positive displacement fluid device that has high volumetric efficiency, total pressure efficiency, or flow rate per unit required horsepower over a wide range of rotational speeds, and is durable.

Another object of the present invention is that when used as a supercharger, it is possible to add a switching device for supercharging/non-supercharging, and
An object of the present invention is to provide a positive displacement fluid device that reduces peak torque at the moment of switching to supercharging.

Still another object of the present invention is to provide a positive displacement fluid device with simple configurations of components.
The goal is to improve productivity and reduce costs by simplifying the structure.

Another object of the present invention is to increase the axial length of a positive displacement fluid device to increase its flow capacity without increasing its radial or lateral dimensions.

Still another object of the present invention is to maintain dynamic balance in a positive displacement fluid device so that vibration does not occur even during high speed rotation.

That is, the present invention has a cylindrical casing, an outer wall surface concentric with the inner wall surface of the cylindrical casing, a fixed cylindrical member disposed in the center of the casing, and an axis between the casing and the fixed cylindrical member. A slot is provided in a space formed between a vertical partition plate extending in a fixed direction, an inner wall surface of the casing, and an outer wall surface of the fixed cylindrical member, and the slot penetrates the partition plate in the radial direction. An eccentric crank section is provided at the front and rear ends of a main shaft rotatably supported via a bearing at the center of the front and rear end walls of the casing, and the above-mentioned pivot cylinder is mounted on the eccentric crank section via a bearing. In a positive displacement fluid device having a rotation prevention mechanism that prevents rotational movement of the rotating cylinder, a balance weight is provided on the main shaft to offset the unbalance caused by the rotating movement of the rotating cylinder, etc. It is characterized in that it is disposed within the central space of the fixed cylindrical member.

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, in which 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 with the closed end. front housing 1
It has a housing 10 consisting of two parts. In addition,
On the outer wall surface of the casing 11 is a protrusion 111 that forms a rectangular opening extending from the vicinity of the front end to the vicinity of the rear end.
A partition plate 14 extending in the axial direction is provided at the center of the opening, and the opening is connected to the suction hole 15 and the discharge hole 16.
It is divided into two minutes. Also, the front housing 12
A main shaft 13 passes through the center of the main shaft 13 .

Here, the configuration will be explained with reference to FIG. 2, which is a horizontal cross-sectional view of the fluid device 1 shown in FIG. Main shaft through hole 121 bored in the center of the front housing 12
Ball bearings 17 and 18 press-fitted into the
It is rotatably supported by. The main shaft 13
A fixed cylindrical member 19 having an outer wall surface concentric with the inner wall surface of the casing 11 is disposed via two bearings 20 and 21 so as to surround the central portion of the casing 11 . That is, the inside of the fixed cylindrical member 19 is a hollow part 191, and support parts 192, 193 extending radially inward are formed at the front and rear ends of the inner wall surface, and the support parts 192, 193 are connected to the bearings 20,
By disposing it on 21, the fixed cylindrical member 19 is supported. Note that the fixed cylindrical member 19 has a third
As shown in the figure or FIG. 5, the inner end of the partition plate 14 that separates the suction hole 15 and the discharge hole 16 is fixed, so that the fixed cylindrical member 19 is stationary and fixed.

Eccentric crank parts 131 and 132 are formed at the front and rear of the main shaft 13 at the same angular position, and on the eccentric crank parts 131 and 132, via bearings 23 and 24, a fixed cylinder whose front and rear ends are closed is formed. A rotating cylindrical member 22 is disposed so as to wrap around the member 19. The rotating cylindrical member 22
As shown in FIG. 7, the eccentric crank parts 131, 13
A circular orbital movement is performed by the rotational movement of 2, but in order to avoid interference with the partition plate 14, a slot 22 extending in the axial direction is provided as shown in FIG. 5 or 7.
1 is formed. Further, a suitable rotation prevention mechanism 25 is disposed between the end face of the swivel cylindrical member 22 and the inner wall surface of the front housing 12 in order to prevent rotational movement of the swivel cylindrical member 22. In this example, this rotation prevention mechanism 25 is shown in FIGS. 2 and 4.
As shown in the figure, a ball coupling mechanism is used. The configuration of the ball coupling mechanism 25 is that the ball coupling mechanism 25 has a hole 251a (a hole 251a in FIG. A swing ring 251 provided with two holes (in this example, two holes are provided), a swing race 252 fixed to the end face of the swing cylindrical member 22 by a pin 253 to provide a rolling surface for the steel balls 256, and a front housing 12
A fixed ring 254 and a front housing 1 are arranged in an annular recess 122 formed on the inner wall surface of the front housing 1 and have a hole 254a similar to that of the swivel ring 251.
A fixed race 255 is fixed to the bottom of the annular recess 121 of No. 2 by a pin (not shown) and provides a rolling surface for the steel balls 256, and a hole 251a of the swivel ring 251.
and a steel ball 256 held between the hole 254a of the fixing ring 254 and the hole 254a of the fixing ring 254.

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, a notch 251A may be provided in a part of the pivot ring 251 as shown in FIG. 8 so that the center of gravity of the pivot ring 251 coincides with the central axis.

In the actual rotating example shown in FIG. 2, among the bearing support parts provided on the fixed cylindrical member 19, the support part 193 on the rear end side is formed integrally with the fixed cylindrical member 19, but the front end part Side support part 192
is formed separately from the core cylindrical member 19 and 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 arranged so that the fixed cylindrical member 19 can be inserted into the rotating cylindrical member 22.
It is formed separately from the main body, 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 131 on the front end side is formed separately from the main shaft 13, and is fixed with a key 28 during the assembly process.

The device described above is assembled in the following order.

First, the bearing 8 is press-fitted into the recess 113 formed in the center of the closed end wall 112 of the casing 11, and the bearing 7 is also press-fitted into the main shaft through-hole 121 of the front housing 12, and fixed in the annular recess 122 formed on the inner wall surface. A ring 254 and a fixing race 255 are arranged and fixed with pins. Next, spindle 1
Eccentric crank part 132 with flange on the rear end side of 3
The rear end closed portion of the rotating cylindrical member 22 is fitted onto the top via the bearing 24, and then the spacer 29 is fitted onto the main shaft 13, and then the rear end side support portion 193 of the fixed cylindrical member 19 is fitted via the bearing 21. Assemble it. After that, the key 27 is inserted into the keyway 133 of the main shaft 13, the balance weight 26 is inserted from the front of the main shaft 13, and then the fixed cylindrical member 1 formed separately
9 is press-fitted into the inner surface of the fixed cylindrical member 19, the bearing 20 is also arranged, and the spacer 30 is
Insert.

A swing race 252 and a swing ring 251 are fixed in advance to the end surface of the closing plate 222 that closes the front end opening of the swing cylindrical member 22 with a pin 253, and a bearing 23 is also press-fitted, and this assembly is attached to the swing cylindrical member. 22 and secure it by caulking. Thereafter, the key 28 is inserted onto the main shaft 13, the eccentric crank 131 is fitted from the front of the main shaft 13, and then the lock nut 31 is tightened in the axial direction. Now, six points are stacked on the main shaft 13 in order from the inner end surface of the eccentric crank part 132 on the rear end side: the spacer 29, the bearing 21, the balance weight 26, the bearing 20, the spacer 30, and the eccentric crank part 131 on the front end side. Locknut 31
This means that it is tightened in the axial direction. The main shaft assembly with the fixed cylindrical member 19 and the rotating cylindrical member 22 is attached to the fixed ring 2.
The main shaft 13 is inserted into the bearing 18 on the front housing 12 with the inner wall surface facing up, with the main shaft 13 inserted into the hole 254a of the main shaft 54. Place the spring washer 32 on the rear end of the main shaft 13, then place a shim 33 of an appropriate thickness on the outer peripheral end surface of the front housing 12, cover it with the casing 11 into which the bearing 17 was first press-fitted, and fix the bolt 34.
Fasten the front housing 12 with.

Next, while looking inside through the opening of the protrusion 111 of the casing 11, turn the slot 221 of the rotating cylinder 22 upward, then the slot 194 of the fixed cylindrical member 19, and
This is completed by inserting the partition plate 14 and fitting it into the slot 194 of the fixed cylindrical member 19.

In this device configured as described above,
All movements of the parts forming the compression chamber are configured to be non-contact. That is, between the outer wall surface of the fixed cylindrical member 19 and the inner wall surface of the rotating cylindrical member 22, and between the outer wall surface of the rotating cylindrical member 22 and the casing 11.
A minimum gap is provided between the inner wall surface and the inner wall surface in order to avoid contact due to eccentricity as a result of cumulative part processing accuracy. Similarly, in the axial direction, the length of the fixed cylindrical member 19 is made smaller than the distance between the inner end surfaces of the rotating cylindrical member 22 within the limits of accuracy so that the end surfaces do not come into contact with each other. The axial gap is shim 3
3 and the length of the spacers 29 and 30, and the movement of the rotating cylindrical member 22 is absorbed by the spring washer 32 disposed between the flange of the eccentric crank part 132 and the inner ring end of the bearing 21. There is.

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. Since 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, the fluid in the space A is discharged through this gap. As is clear from the sequence of FIGS. 6c to 6f, the rotating cylindrical member 22
Ejection continues as the body 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 of the contact point P ( _P1 to _P6 ). As the fluid in the 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 as shown in FIGS. 6a to 6d. while taking in fluid, crank angle 180
At point _Q1 at ゜+α゜ (FIG. 6f), sealing is achieved from the suction side and fluid discharge begins.
As is clear from FIGS. 6g, h, a, b, and c, the volume of this space B (indicated by B in FIGS. 6a to 6c) decreases with the movement of the rotating cylindrical member 22, and the volume of the space B (indicated by B in FIGS. Drainage continues and new fluid intake begins on the opposite side via 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 fixed 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 2α° of the slot 221 formed in the rotating cylindrical member 22 is designed to be minimized to the extent that there is no interference with the partition plate due to the rotation of the rotating cylinder, this gap will become a device with a pressure ratio of 1 to 2. If so, it's not a big problem. In particular, this device uses a rotating cylindrical member with a relatively small radius, so it can rotate at high speed without consuming a large amount of horsepower, so the time that the intake and exhaust holes communicate can be shortened, reducing large losses. It won't happen. The reason why this fluid device can be used at high speed rotation is that 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 come very close together. The suction and exhaust pressures are partitioned, and the movement of air due to the rotation of the main shaft does not involve shearing of the air as in vane rotary type devices. 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 the casing 11, which will also allow communication between the suction and exhaust holes, but even in this state, the performance at high speed rotation will be satisfactory for the reasons mentioned above. Become something.

FIG. 9 shows another embodiment of the present invention,
This is a partial modification of the support structure of the fixed cylindrical member 19. That is, the fixed cylindrical member 19 supports the main shaft 13 by the support portion 193 provided in the center of the internal cavity.
It is supported on the top via a bearing 36. At this time, the balance weight 26 disposed on the main shaft 13
a and 26b are arranged on both sides of the support part 193.

FIG. 10 shows yet another embodiment in which the support structure of the fixed cylindrical member 19 has been changed, and the fixed cylindrical member 19 becomes independent within the casing 11 via the partition plate 14 by increasing the rigidity of the partition plate 14. and stand still
Fixed.

As described above, in the fluid device of the present invention, the rotating cylindrical member is disposed in the space formed between the cylindrical casing and the fixed cylindrical member fixed to the center of the casing, and the rotating cylindrical member Since fluid is sucked and discharged by rotating the members, the component parts can have a simple shape and a simple structure, which improves productivity. It is possible to improve the performance and reduce costs.

Furthermore, since the fluid suction and discharge operation does not involve shearing of air, it is possible to drive without consuming large horsepower even at the start of supercharging operation.

Furthermore, since the balance weight is disposed in the hollow portion within the fixed cylindrical member, dynamic balance during high-speed rotation can be maintained without increasing the size of the entire device.

[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 horizontal sectional view of the fluid device shown in FIG. 1, FIG. 3 is a cross-sectional view of FIG. 2 is a sectional view, FIG. 5 is a sectional view of FIG. 7 is a perspective view of the pivoting cylindrical member, FIG. 8 is a perspective view of the pivoting cylindrical member to show another embodiment of the pivoting cylindrical member, and FIGS. 9 and 10 FIG. 3 is a sectional view showing another embodiment of the present invention. 11... Cylindrical casing, 12... Front housing, 13... Main shaft, 131, 132...
Eccentric crank part, 14... Partition plate, 19... Fixed cylindrical member, 191... Cavity part, 22... Rotating cylindrical member, 221... Slot, 25... Rotation prevention mechanism, 26... Balance weight.

Claims (1)

[Claims] 1. A housing comprising a cylindrical casing and an end plate disposed on an end face 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. a rotating cylindrical member, a pair of eccentric crank parts are formed on the main shaft supported at the front and rear ends of the housing, and the rotating cylindrical member is supported on the eccentric crank parts via bearings. In a positive displacement fluid device that makes a rotating movement, a hollow part is formed in the center of the fixed cylindrical member, and a balance weight is disposed on the main shaft within the hollow part to offset the unbalance caused by the turning movement. A rotating cylindrical piston type positive displacement fluid device characterized by: 2 A protrusion is formed on the outer surface of the cylindrical casing to form a rectangular opening extending along the axial direction from near the front end to near the rear end, and within the opening is a partition with one end fixed on the fixed cylindrical member. The rotating cylindrical piston type positive displacement type according to claim 1, wherein the other end of the plate is arranged to extend in the axial direction, and the opening is divided into two into an intake hole and a discharge hole. Fluid equipment. 3. The fixed cylindrical member according to claim 1 or 2, wherein the fixed cylindrical member is supported on the main shaft via a bearing by a support portion formed on the inner wall surface so as to extend radially inward. Swivel cylindrical piston type positive displacement fluid device. 4. In order to secure a gap between the front and rear end surfaces of the rotating cylindrical member and the inner wall surfaces of the casing and front housing, a flange portion is formed on the rear end side of the eccentric crank part provided on the rear end side of the main shaft, and An elastic body is disposed between the support bearing and the flange portion to urge the rotating cylindrical member toward the front housing, and to adjust the axial position of the fixed cylindrical member between the eccentric crank portion and the bearing to maintain the center of the fixed cylindrical member. 4. The rotating cylindrical piston type positive displacement fluid device according to claim 3, wherein the swiveling cylindrical piston type positive displacement fluid device is determined by a spacer disposed in the cylindrical piston. 5. The rotating cylindrical piston type positive displacement fluid device according to claim 1, wherein the fixed cylindrical member is fixed concentrically to the inner wall surface of the casing by a partition plate.