JPS6354148B2 - - 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 these velocity formulas or volume ratios. 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. There is a growing demand for compressors or blowers having characteristics intermediate between velocity type and 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 a belt, the increase in engine output obtained by supercharging is due to the power required to drive the supercharger. However, it is difficult to obtain a supercharger that pumps air with high volumetric efficiency over a wide rotation speed range and has high total pressure efficiency, so it is difficult to obtain a supercharger that has a small net power increase. This has the drawback of requiring large costs 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.

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. It has a rotating cylindrical member with 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. In the type fluid device, it is not possible to make the total length of the partition plate for partitioning the discharge side and the suction side equal to the total length of the rotating cylindrical member that performs the rotating motion.

In other words, the total length of the partition plate must be reduced by the thickness of the side plate of the rotating cylindrical member, which eliminates the disadvantage that a complete partition between discharge and suction cannot be achieved and compressed fluid flows back through this part to the suction side. had.

In order to solve this problem, the side plate of the swivel cylindrical member is eliminated, the partition plate and the swivel cylindrical member are made to have the same length, and the side plate is replaced with the diameter of the swivel cylindrical member + (4 x radius of swing motion). Large side plates having at least the following dimensions shall be attached on both sides of the pivoting cylinder member. However, doing so has the problem that the original objective of miniaturization must be sacrificed.

In order to eliminate such defects, the present invention provides a unique partitioning structure between the partition plate and the side plate portion of the rotating cylindrical member, and aims to maintain a perfect partition (seal) while being miniaturized.

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

That is, the present invention provides a housing consisting of a cylindrical casing and a front end plate disposed on one end surface of the casing, and a fixed cylindrical member disposed in the center of the casing and having an inner cylindrical surface concentric with the inner wall surface of the casing. , a vertical partition plate extending in the axial direction between the casing and the fixed cylindrical member, and a slot arranged in the annular space formed between the casing and the fixed cylindrical member and passing through the partition plate in the radial direction. and a rotating cylindrical member whose front and rear ends are closed, and a pair of eccentric crank parts are formed at the front and rear of a crankshaft that extends in the center of the housing and is supported by bearings at the front and rear ends of the housing, In a positive displacement fluid device in which the swivel cylindrical member is supported on the eccentric crank portion via a bearing, and the swivel cylindrical member performs a fluid suction and discharge operation by rotating the swivel cylindrical member, both end portions of the swivel cylindrical member correspond to the slots. A notch is provided in which the recessed portions having a dimension larger than the radius of rotation of the swivel cylindrical member face each other and both upper end portions are eaves, and the cylindrical swivel member is located within the notch at both end components of the partition plate. A partition is provided with recesses having dimensions larger than the turning radius that face each other in opposite directions, and both ends of the lower portion are protrusions, so that at least a part of the turning trajectory at the tip of the notch eaves matches the recess of the partition. This is a rotating cylindrical piston type positive displacement fluid device in which a part of the orbit of the recessed part of the notch is located at the tip of the protruding part of the partition. It was possible to completely partition the compressed fluid that was flowing back to the side.

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

Fig. 1 is a right side view of a positive displacement fluid device showing an embodiment of the present invention, Fig. 2 is a longitudinal sectional view of the same, and Fig. 3 is an exploded perspective view of the same. The housing 100 includes a cylindrical casing 1, a front end plate 8 installed at one end of the casing 1, and a rear end plate 7 installed at the other end.

The front end plate 8 has a through hole 10 through which the main shaft portion 56 of the crankshaft 6 is inserted.
1, and a circular recess into which the front shaft bearing 11 is inserted is provided on the back side of the through hole 101.

The rear end plate 7 is provided with a circular recess into which the rear shaft bearing 13 is inserted and a recess into which the boss of the swivel cylindrical member 2 moves.

The casing 1 has a substantially hollow cylindrical shape,
As described above, the front end plate 8 and the rear end plate 7 are joined by fitting into both openings, and fixed by housing fixing bolts 16. The casing 1 has a fluid suction hole 51 and a fluid discharge hole 52 in its upper part, and a flat surface is provided for fitting with an external system connected to the discharge hole 52 and the suction hole 51. Furthermore, a plurality of screw through holes and positioning pin holes are provided in this upper flat part, and the fixed cylindrical member 3 is fixed concentrically to the casing 1 via the partition plate 4 and the partition plate 4.

The crankshaft 6 consists of a main shaft part 56, a front crank part 53, a balance weight 55, and a rear crank part 54. It is rotatably supported by a shaft bearing 11 and a rear shaft bearing 13. Although the crankshaft 6 is formed integrally in the illustrated example, it may be provided with a separate balance weight 55, for example.

The front end plate 8 also has a main shaft portion 56.
It has a sleeve 57 extending forward so as to surround it. The sleeve 57 is attached to the front end plate 8
Although not shown, an electromagnetic clutch is provided via a bearing. (The electromagnetic clutch is equipped with a pulley, and the rotation is transmitted from an external drive source, such as an engine, by a transmission means such as a belt, and this rotational force is transmitted to the main shaft 56 in an intermittent manner.The electromagnetic clutch is an absolutely necessary means. (For example, the pulley may be directly attached to the main shaft 56.) In addition to the crankshaft 6, the housing 100 includes a rotating cylindrical member 2, a fixed cylindrical member 3, a partition plate 4, and a rotation prevention mechanism 60. There is.

The rotating cylindrical member 2 is composed of a rotating cylinder 61, a side plate 5, a front drive bearing 12, and a rear drive bearing 14.

The rotating cylinder 61 is a hollow cylinder having a slot (linear notch) 152 through which the partition plate 4 passes, and has a bottom or side surface 157 only on the side facing the front end plate 8, and the other side is open. It has a hole.

The front drive bearing 12 is fitted into the opening at the center of the side surface 157, and the side surface 157, whose position corresponds to the slot (notch) 152, has an eyebrow-shaped shape with semicircular arcs facing each other. An eyelash-shaped notch 151 is provided.

The side plate 5 is fitted into the open end of the rotating cylinder 61 and fixed by means such as screws.

The side plate 5 has almost the same shape as the side part 157, and the rear drive bearing 14 is fitted into the opening in the center, and the side plate 5 has a cocoon-shaped notch 150 having the same shape as the cocoon-shaped notch 151 of the side part 157. will be established.

The fixed cylindrical member 3 is a hollow cylinder, and a plurality of screw holes and positioning pin holes for fixing to the casing 1 via the partition plate 4 are bored in the cylindrical surface. Further, a hole is provided in the center of the side surface for the crankshaft 6 to pass through. The illustrated structure is made in one piece, but since this requires casting using a core or boring and turning, it may be formed in two parts.

The partition plate 4 has a discharge hole notch 156, a suction hole notch 155, and χ-shaped partition pieces 153, 154, and supports the fixed cylindrical member 3 while partitioning the discharge chamber and the suction chamber. . The partition plate 4 is the third
In addition to the shape shown in the figure, it may be formed into a flat plate shape as shown in FIGS. 7a and 7b, or may be formed as shown in FIG. 7c. Also, from the total radial length of the partition plate 4, the χ-shaped partition piece 1
The length after subtracting the wall thickness of 53 and 154 corresponds to the entire length of the fixed cylindrical member 3 and the hollow part of the rotating cylindrical member 2, and the wall thickness of the χ-shaped partition pieces 153 and 154 is the same as that of the side plate 5. The thickness is equal to the wall thickness of the side surface portion 157 of the rotating cylinder 61.

χ-shaped partition pieces 153, 154 and cocoon-shaped notch 15
0,151, as explained in FIGS. 8 and 9, has a geometric shape that allows contact (sealing) at least at one point at any time during the pivoting movement of the rotating cylindrical member 2,
A seal is maintained to prevent the discharged fluid from flowing back to the suction side via the side surface portion 157 and the side plate 5.

Although many other types of rotation prevention mechanism 60 are known, such as a crank coupling using a crank-shaped member, the illustrated example is an example using a ball coupling mechanism, and the front end plate 8
The rotation of the rotating cylinder 61 is prevented by the balls 10 sandwiched between a plurality of circular grooves 160 for ball guides provided on the back surface of the rotating cylinder 61 and the side surface 157 of the rotating cylinder 61, and only the revolution movement is performed. Note that if the ball guide circular groove 160 is made of a light alloy material, there is a problem in durability, so in the illustrated example, the ball support metal 9 is inserted into the circular groove 160 to improve durability. In the illustrated example, the rotation prevention mechanism 60 may be provided between the front end plate 8 and the side surface portion 157 of the swing cylinder 61, or may be provided on both at the same time.

Next, the assembly of the above structure will be described. First, the fixed cylindrical member 3 is fixed to the casing 1 via the partition plate 4 using bolts 14 and positioning pins 15. Next, the crankshaft 6 is attached to the fixed cylindrical member 3.
The side plate 5 and the rotating cylinder 61, into which the bearings 14 and 12 are press-fitted, are inserted from both open ends of the casing 1 so as to wrap around the fixed cylindrical member 3, and at the same time, the side plate 5 and the rotating cylinder 61 After fixing the rotating cylinder 61 into which the crank parts 54, 53 of the crankshaft 6 are fitted to the bearings press-fitted into the side plate 5, the front end plate 8 is attached to the casing 1 via the balls 10, and the rear end plate 7 is attached to the casing. Each is fixed to 1. Fixed cylindrical member 3, partition plate 4 and casing 1
Although it is difficult to process, it is also possible to implement it in an integrated manner.

Next, the suction and discharge operations of fluid in this device will be explained with reference to FIGS. 4a to 4h.

In Fig. 4 a to h, the crank angle of the main shaft 6 is 0°,
α゜, 90゜, 180゜−α゜, 180゜, 180゜＋α゜, 270゜, 360゜−
The position of the pivoting cylinder member 2 at α° is shown.

Figure 4 a shows the crank angle 0° [below b is α°, c is
90°, d is 180° - α°, e is 180°, f is 180° + α°, g
is 270°, h is 360°-α°], and for convenience, the crank angle of 0° is the fluid intake end point of chamber A in the drawing, that is, the space formed by the rotating cylindrical member 2 and the inner surface of the casing 1. do. Note that the space in which the high-pressure side fluid exists is indicated by a dot in the figure. At a crank angle of 0°, chamber A communicates with the high pressure side at the moment;
The pressure in the room is approximately atmospheric pressure (in the case of atmospheric air intake). The B chamber is a space formed between the fixed cylindrical member 3 and the inner surface of the rotating cylindrical member 2, and is approximately half divided into a high pressure side and a low pressure side.

In b, when the crank angle has moved by a small angle α from the state in a, chamber A is completely communicated with the high pressure side, but is sealed from the low pressure side.

c is a state in which the crank angle has advanced by about 90°,
The sealing point on the low pressure side of chamber A gradually moves to the high pressure side while decreasing its volume.

d is a crank angle point of 180°-α° (α° is a minute angle), which is just before the end of the stroke in which chamber B takes in suction fluid. Chamber B is still open to the low pressure side but sealed to the high pressure side.

e is a crank angle of 180°, and this is the moment when chamber B is slightly opened to the high pressure side. This is A at a
Similar to the case of a chamber, even if it opens to the high pressure side, the time is extremely short, so there is little backflow of fluid. Therefore, the inside of room B is still maintained at approximately atmospheric pressure.

f is a state where the crank angle is 180°+α°, and the B chamber is in communication with the high pressure side, and the B chamber is under high pressure, but is sealed from the low pressure side.

g is at a crank angle of 270°.

h is a state where the crank angle is 360°-α°, and the suction fluid intake stroke of chamber A is about to end. Chamber A communicates with the low pressure side, but is sealed with respect to the high pressure side.

The pressure conditions and seal conditions in chambers A and B during one crank rotation have been explained above, but to summarize the above, except for the moment when the transition from the end of the discharge stroke to the suction stroke occurs, the discharge side (high pressure side) and the suction side ( It is always separated from the low pressure side), and the communication at the moment of transition from the discharge stroke to the suction stroke is extremely short, and the generated gap is small, so it can be said that there is no problem in applications where the pressure difference is small.

To explain this in more detail, in b, in the process of turning the rotating cylindrical member 2 by α°, one outer wall surface of the rotating cylindrical member 2 and the inner wall surface of the casing 1 come into contact at a point P, and a sealed space is created. A is formed and a gap is created between the other outer wall surface of the rotating cylindrical member 2 and the inner wall surface of the casing 1, so the fluid in the space A begins to be discharged through this gap, and the sequence shown in FIGS. As is clear from the following, the discharge continues as the rotating cylindrical member 2 moves. The volume of the space A decreases as the rotating cylindrical member 2 moves, and new fluid intake begins on the opposite side via the contact point P. This space A
As the fluid inside is discharged, the volume of the space B formed between the outer wall surface of the fixed cylindrical member 3 and the inner wall surface of the rotating cylindrical member 2 expands as shown in FIGS. 4a to 4d, and takes in the fluid. At point Q in FIG. 4 at a crank angle of 180° + α°, sealing is achieved from the suction side and fluid discharge begins. Figure 4 g, h, a,
As is clear from b and c, the volume of this space B decreases as the rotating cylindrical member 2 moves, fluid discharge continues, and new fluid intake begins on the opposite side of the contact point Q. Ru.

In the fluid suction and discharge cycle as described above, a gap is created between the outer wall surface of the rotating cylindrical member 2 and the inner wall surface of the casing 1 when the crank angle is between 360° - α° and 360° + α°, and the crank angle is between 180° - α° and 180° + α°, there is a gap between the inner wall surface of the rotating cylindrical member 2 and the outer wall surface of the fixed cylindrical member 3, and if considered quasi-statically, this is due to the gap. The suction hole 51 and the discharge hole 52 will be in communication with each other. However, the slot 1 formed in the rotating cylindrical member 2
If the design is such that the opening angle of 52 is minimized, this gap will not be a big problem if the device has a pressure ratio of 1 to 2.

In addition, the compression mode is a so-called isobaric change in which the fluid is simply pumped out without an internal compression ratio, as shown in Figure 5.The power loss is greater than in normal adiabatic change, but it is used for applications with a small compression ratio. There is no difference in this, and it is usually used in applications where the compression ratio is small.

Figure 5 shows the relationship between volume and pressure in the case of isobaric compression (shown by the solid line) and the case of adiabatic compression (shown by the broken line).The required energy difference △Q is the area
The difference between ACDE and area BCDE, that is, △Q=(P _d −
P _s )・V _MAX −∫ ^Pd _Ps V _dp . In this case P _d P _s
(for low compression ratio applications), △Q≒O, and loss is not a problem.

6a and 6b show the positional relationship between the conventional partition plate 41, fixed cylindrical member 31, rotating cylinder 611, and side plate 51 (rear drive bearings etc. are omitted). The axial length must be shorter than the total length of the pivoting cylindrical member by the thickness t of the side plate 51. In other words, the partition plate 41 must not be within the range of movement of the side plate 51 in order for the side plate 51 to make a revolution.

Therefore, the area l×t indicated by the cross line in FIG.
opens as a gap. In the figure, l is the side plate 5
It changes from 0 to _2rO ( _rO : orbital radius) depending on the motion position of 1. The gaps shown existed on both sides of the pivot cylinder 611 and were very problematic in terms of compressed fluid leakage.

In view of this point, the present invention solves the above problem by using a structure as shown in FIG. 7 (rear drive bearing 14 and the like are omitted). (Hereafter, Section 7
9, the partition piece of the partition plate and the notch part of the rotating cylindrical member are connected to one partition piece 153 and the notch part 1.
50, it goes without saying that the other partition piece 154 and cutout portion 151 have exactly the same configuration. ) This will be explained below with reference to FIG.

The partition plate 4 and the fixed cylindrical member 3 are fixed using bolts, and partition pieces 153 having semicircular arcs facing each other in an x-shape are provided at both ends of the partition plate 4 to connect the partition plate 4 and the fixed cylinder. It is fixed so as to protrude outward from the side surface of the member 3. The combined body of the partition plate 4 and the fixed cylindrical member 3 shown in FIG. 7b is shown in FIG. 7a.
As shown, it is located so as to be covered by the rotating cylinder 61 and the side plate 5, and the slot 15 of the side plate 5
At a position corresponding to 2, an eyebrow-shaped notch 150 with semicircular arcs facing each other at a distance is provided.
This rotating cylinder 61, fixed cylindrical member 3, and partition plate 4
are located at the same position in the axial direction, and the axial dimensions of the fixed cylindrical member 3 and the partition plate 4 are approximately the same and slightly smaller than the axial dimension of the rotating cylinder 61. The x-shaped partition pieces 153 are located at the same position in the axial direction with respect to the side plate 5 and have the same plate thickness.

FIG. 8 shows the positional relationship between the cocoon-shaped notch 150 of the side plate 5 and the x-shaped partition piece 153 with respect to the crank angle. From a to d, changes are shown at every 90° crank angle, but no matter what position the crank angle is in, the high pressure side and low pressure side never communicate.
Movement of the side plate 5 will be performed while maintaining the seal. In other words, the crank angle of the main shaft 6 is from 0°
While rotating through 90 degrees and 180 degrees, the eaves 200 protruding forward at the upper end of the left recess 201 formed by the semicircular arc of the cocoon-shaped notch 150 in the drawing changes to the semicircular recess 203 on both sides. The high-pressure fluid is fed into the discharge hole while contacting the left recess 202 of the x-shaped partition piece 153. At this time, the lower end protrusion 203 of the partition piece 153 also comes into contact with the recess 201 of the notch 150, forming a double seal to seal the high pressure fluid on the left side and the low pressure fluid on the right side. However, in this case, as can be seen from d, a portion of the high-pressure side fluid remains in the eyebrow-shaped notch 150 and is returned to the low-pressure side. However, since the volume of this portion is sufficiently small compared to the total displacement volume, this does not pose any problem in a blower with a low compression ratio.

Next, a few specific examples for carrying out the present invention will be explained.

The present invention always creates at least one contact point (sealing point) on one side (two on both sides) between the notch at both ends of the rotating cylindrical member and the partition at both ends of the partition plate to prevent pressure fluid from flowing back to the suction side. This is how it was done.

Figure 9 a and b show two locations on one side (four locations on both sides)
The X-shaped partition pieces 153 provided at both ends of the partition plate 4 and the eyebrow-shaped notches provided at both ends of the rotating cylindrical member 2 (side plate 5 in the drawing) 150 will be provided. Partition piece 153
is the turning motion radius of the turning cylindrical member 2 at a
The recessed portions 202 of a semicircular arc equal to r _O are made to face each other on both sides, and protrusions 203 are provided at both ends of the lower part.
The radius of 2 is defined as [swivel radius r _O + cutout eave 20
The radius α of the thickness is 0]. On the other hand, the cutout part 150 is made by making semicircular recessed parts 201, both of which are equal to the turning radius r _O , facing each other at a distance. It is rounded with an arc of α. Furthermore, the partition piece 153 is positioned on a line extending from the center of the crankshaft 6 between the tip of the x-shaped lower protrusion 203 and the tip of the upper protrusion 206, and the curved surface of the semicircular recess 202 is aligned with the lower protrusion 203 and the tip of the upper protrusion 206. It is formed between the notch portion and the upper protrusion 206 so as not to interfere with the turning movement of the notch eave portion 200.

As described above, when the rotating cylindrical member 2 makes a rotating movement at a, the eaves part 20 of the notch 150
0 is a partition piece 1 that makes a turning motion drawing an orbit with a radius r _O and comes into contact with this to form a contact point (sealing point).
Since the semicircular arc recess 202 of 53 is also created with a radius r _O , no interference will occur. Furthermore, since the semicircular recess 201 of the notch 150 as a whole also makes a turning movement with a radius of r _O , the partition piece 1
The protrusions 203 at both ends of the lower part 53 also form contact points (sealing points) without causing interference. In addition, in b, since the eaves part 200 of the notch part 150 is rounded with a radius α, the recessed part 202 of the partition piece 153 is also a semicircular arc larger by the radius α, and as in a, there are two contact points on one side (seal point).

Therefore, the oppositely opposed recesses 2 of the partition piece 153
02, the turning radius r _O of the turning cylindrical member 2 in which the eaves part 200 of the notch part 150 makes a turning movement is set to the minimum, and it is formed with a recessed part larger than that according to the thickness of the eaves part 200, so that the eaves part 200 turns. It will match a part of the trajectory of movement. Further, the recessed portions 201 of the notch portions 150 that face each other also have a turning radius r _O of the turning cylindrical member 2 .
If the tip is rounded for reinforcement like the eaves part 200, the radius of the semi-circular recessed part can be made larger according to the increased thickness, and the turning movement as a whole can be improved. When doing so, a part of the turning trajectory is caused by the protrusions 20 at both lower ends of the partition piece 153.
Position it at the tip of 3.

The above a and b are the eaves 200 of the notch 150, the semicircular arc that is the recess 202 of the partition piece 153, the semicircular arc that is the recess 201 of the notch 150, and the protrusion 203 of the partition piece 153. (4 locations on both sides)
When providing a contact point (sealing point), it is clear that this contact point (sealing point) can be provided at one location (two locations on both the front and rear sides) to prevent backflow of pressurized fluid to the suction side. It is.

One contact point (sealing point) is the notch 150
eaves portion 200 and the recessed portion 202 of the partition piece 153, or the recessed portion 201 of the notch portion 150 and the partition piece 15
However, in the former case, the recess 202 of the partition piece 153 that the eaves part 200 contacts is the same as the turning radius of the rotating cylindrical member 2, or depending on the thickness of the eaves part 200. A semicircular arc with an increased radius is formed so that the trajectory of the tip of the eaves section 200 passes through this semicircular arc, thereby creating a contact point (sealing point).
However, the recessed part 201 of the notch 150 may have any shape as long as the tip of the protruding part 203 of the partition piece 153 does not come into contact with it. It may be a circular arc or any other shape.

Next, the recess 201 of the notch 150 and the partition piece 15
3. This is a case where a contact point (sealing point) is formed only between the tips of the protrusions 203 on both sides of the lower part, but when the rotating cylindrical member 2 rotates with a radius r _O , the notch 15
The radius r O of the recess 201 is such that the recess 201 is in constant contact with the tip of the protrusion ₂₀₃ .
3. Formed by a semicircular arc with a radius of length added with a dimension corresponding to the thickness of the tip. At this time, the tip of the protruding portion 203 is always located within the turning movement locus drawn by the semicircular recessed portion 201 of the notch portion 150 as a whole.
In other words, a part of the orbit of the semicircular curved surface of the notch 150 is located at the tip of the protrusion 203. The recessed portion 202 of the partition piece 153 is
In this case, as long as the eaves part 200 of the cutout part 150 does not come into contact with each other, the shape may be any shape including a semicircular arc. For example, as shown in FIG.
A lateral portion 205 may be provided at the bottom, and the tip portion of the lateral portion 205 may be a protruding portion 203.

In the above explanation, the partition pieces and notches are also explained by the notches 150 and partition pieces 153 on the rear side of the rotating cylindrical member 2, that is, the side plate 5, as is clear from the reference numbers in the drawings. side part 157
It is clear that this contact point (sealing point) is also formed at the same time on the notch piece 154,
Furthermore, although an example is shown in which partition pieces 153 and 154 are provided at both ends of the partition piece 4, the same effect can be obtained even if both ends of the partition piece 4 are processed. Although the fixed cylindrical member 3 is omitted from the lower part and not shown in the drawing, it is natural that the fixed cylindrical member 3 performs sealing within the range of movement of the notch 150.

Further, in the embodiment, the cutout portions 150, 1
51, the lower protrusion 203 of the partition pieces 153, 154, and the eaves 200 of the notches 150, 151 and the depression 202 of the partition pieces 153, 154.
Although it has been explained that a contact point (sealing point) is formed during the pivoting movement of the pivoting cylindrical member 2, the contact point does not necessarily have to be made, but a sufficiently small gap that substantially prevents fluid leakage may be created.

As described above, the present invention has a housing consisting of a cylindrical casing and a front end plate disposed on one end surface of the casing, and an inner cylindrical surface disposed in the center of the casing and concentric with the inner wall surface of the casing. a fixed cylindrical member; a vertical partition plate extending in the axial direction between the casing and the fixed cylindrical member; A rotating cylindrical member having a slot formed therethrough and closed at the front and rear ends, and a pair of eccentric crank parts are formed at the front and rear of the crankshaft, 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 on the eccentric crank portion via a bearing and the rotating cylindrical member is rotated to perform a fluid suction and discharge operation, the rotating cylindrical member has a corresponding slot. A notch is provided at both end components of the partition plate, and a notch is provided at both end portions of the partition plate, and a recess having a dimension larger than the radius of rotation of the rotating cylindrical member faces each other, and both upper end portions are eaves. A partition is provided in which recesses having dimensions larger than the radius of rotation of the cylindrical member are opposed to each other and both ends of the lower portion are protrusions, so that at least a part of the rotation trajectory at the tip of the notch eaves matches the recess of the partition. Alternatively, since this is a rotating cylindrical piston-type positive displacement fluid device in which a part of the orbit of the notch recess is located at the tip of the protrusion of the partition, when the rotating cylindrical member rotates, the rotating cylindrical member Because the depressions of the notches provided at both ends of the partition plate are always in contact with the protrusions formed at the bottom of both ends of the partition plate, or the eaves of the cutout parts are always in contact with the depressions of the parts at both ends of the partition plate, Sealing is performed at at least one point (two points including the front and rear sides) at both end portions, and the high-pressure fluid does not flow back to the suction side, making it possible to obtain extremely high volumetric efficiency.

Furthermore, the present invention requires only slight processing of both ends of the partition plate and both ends of the slot of the rotating cylindrical member, or the attachment of members processed into the desired shape, so that the discharge side and the suction side can be partitioned off with an extremely simple configuration. And to achieve this partition,
A small and lightweight fluid device can be obtained without requiring a large side plate for the rotating cylindrical member.

[Brief explanation of the drawing]

Fig. 1 is a right side view showing an embodiment of the rotating cylindrical piston type positive displacement fluid device of the present invention, Fig. 2 is a vertical sectional view showing the internal structure, and Fig. 3 is an exploded perspective view showing the assembled state of each component. , Fig. 4 a to h are explanatory diagrams showing the suction and discharge states of fluid at different crank angles of the main shaft, Fig. 5 is a diagram showing the relationship between volume and pressure in equal pressure compression, and Fig. 6 a ,b
7 is a perspective view showing the positional relationship of a conventional partition plate, a fixed cylindrical member, a rotating cylinder, and a side plate, and FIGS. A perspective view showing the positional relationship between the rotating cylinder and the side plate provided with the notch, FIGS. 8a, b,
c and d are explanatory diagrams showing the positional relationship between the notch and the partition in the embodiment of the fluid device of the present invention and the crank angle at 90° intervals, and Fig. 9 a, b, and c are the notches in the embodiment of the fluid device of the present invention. It is an explanatory view showing an example of size and shape of a part and a partition part. 1...Casing, 2...Swivel cylindrical member, 3...
... Fixed cylindrical member, 4 ... Partition plate, 5 ... Side plate,
6...Crankshaft, 7...Rear end plate, 8...Front end plate, 12...
Front drive bearing, 14...Rear drive bearing, 51...Suction hole, 52...Discharge hole, 53...Front crank part, 54...Rear crank part, 60...Rotation prevention mechanism, 61...Swivel cylinder, 100... Housing, 150, 151...
Notch portion, 152... Slot, 153, 154...
...Partition piece, 157...Side part, 200...Eave part,
201... Recess of notch, 202... Recess of partition piece, 203... Lower protrusion of partition piece, 204
... Vertical section, 205 ... Horizontal section, 206 ... Upper protrusion of partition piece.

Claims (1)

[Claims] 1. A housing consisting of a cylindrical casing and a front end plate disposed on one end surface of the casing, and a fixed cylinder disposed in the center of the casing and having an inner cylindrical surface concentric with the inner wall surface of the casing. a vertical partition plate extending in the axial direction between the casing and the fixed cylindrical member; and an annular space formed between the casing and the fixed cylindrical member;
It has a rotating cylindrical member that forms a slot that penetrates the partition plate in the radial direction and is closed at the front and rear, and extends in the center of the housing and supports the front and rear of the crankshaft that is supported by bearings at the front and rear ends of the housing. In a positive displacement fluid device, in which a pair of eccentric crank parts are formed, the rotating cylindrical member is supported on the eccentric crank part via a bearing, and a fluid suction and discharge operation is performed by rotating the rotating cylindrical member. , at both ends of the swivel cylindrical member to which the slot corresponds, a notch is provided at both ends of the partition plate, with recesses having dimensions larger than the radius of swivel motion of the swivel cylindrical member facing each other, and with both upper end portions serving as eaves. A partition is provided within the notch and has concave portions having dimensions larger than the radius of rotation of the rotating cylindrical member that face each other in opposite directions, and has protrusions at both ends of the lower portion, so that at least part of the orbit of the tip of the eave of the notch is provided. A rotating cylindrical piston type positive displacement fluid device in which a portion of the notch portion coincides with a recessed portion of a partition portion, or a portion of the orbit of the recessed portion of the notch portion is located at a position of a tip of a protruding portion of the partition portion. 2. The recesses of the notches at both ends of the swivel cylindrical member and the recesses of the partitions at both ends of the partition plate are made into semicircular arcs with a radius of rotation greater than the radius of rotation of the swivel cylindrical member, and a part of the tip of the eave of the notch is rotated. The rotating cylindrical piston type volume according to claim 1, wherein the orbit matches the recess of the partition, and a part of the orbit of the recess of the notch is located at the tip of the protrusion of the partition. type fluid device. 3. The recesses of the notches at both end portions of the swivel cylindrical member are semicircular arcs that are larger than the radius of swivel motion of the swivel cylindrical member;
A patent in which the concave portions of the partitions at both ends of the partition plate are formed into an arbitrary shape larger than the radius of rotation of the rotating cylindrical member, so that a part of the orbit of the concave portion of the notch is located at the tip of the protruding portion of the partition. A rotating cylindrical piston type positive displacement fluid device according to claim 1. 4. The recesses of the notches at both end portions of the swivel cylindrical member are made into an arbitrary shape larger than the radius of rotation of the swivel cylindrical member, and the recesses of the partitions at both ends of the partition plate are shaped into semicircular arcs that are larger than the radius of swivel movement of the swivel cylindrical member. 2. The rotating cylindrical piston type positive displacement fluid device according to claim 1, wherein a part of the orbit of the notch eaves matches the recess of the partition. 5. The rotating cylindrical piston type according to claim 1 or 3, wherein the partition portions at both ends of the partition plate are provided with a vertical portion at the top and a horizontal portion at the bottom, and the tip portion of the horizontal portion is a protruding portion. Positive displacement fluid device. 6. A rotating cylindrical piston-type volume according to claim 1, 2, 3, 4, or 5, in which the notch of the swiveling cylindrical member is shaped so as to face each other with semicircular arcs separated from each other. type fluid device. 7. Claims 1 or 2 or 3 or 4 or 6 in which the partitions at both ends of the partition plate are formed into a substantially χ-shape with semicircular arcs facing oppositely left and right. The rotating cylindrical piston type positive displacement fluid device as described in .