JP2003021075A - Rotary type cylinder device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent leakage of fluid from an abutting part of a piston on a cylinder member and to reduce loss in converting fluid energy to rotation motion or the rotation motion to the fluid energy. SOLUTION: This cylinder device comprises the rotating cylinder member 2 that has cylinder chambers 22 and 23 so as to pass through a rotation axis O and rotates around the rotation axis O, pistons 3 and 4 moving reciprocatively and linearly in the cylinder chambers 22 and 23, a piston holding member 5 that holds the pistons 3 and 4 and rotates about a rotation center X decentering from the rotation axis O of the rotating cylinder member 2, and a casing 6 that supports the rotating cylinder member 2 rotatably and has at least one inlet 61 and at least one outlet 62. The pistons 3 and 4 are held at positions a certain distance away from the rotation center X of the piston holding member 5 and rotatably around the positions.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cylinder device that can be used as a pump, a compressor, a fluid motor or the like, and more particularly to a rotary cylinder device in which a piston moves in and out of a cylinder chamber due to rotational movement.

The term "rotary type cylinder device" used in the present specification includes not only devices that perform mechanical work by using fluid energy, but also devices that compress and pump fluid by using rotational energy. I use it as a thing.
That is, the term "rotary type cylinder device" means a generic name for devices such as a rotary pump, a rotary compressor, and a fluid motor.

[0003]

2. Description of the Related Art Conventionally, a rotary pump using a gear-shaped rotor has been known as a pump of a type in which a rotor is rotated and a fluid is pushed out by its displacement. However, in the case of this pump, it is difficult to form the tooth profile of the rotor, which causes a cost increase. Therefore, in order to solve this drawback, the applicant has developed a rotary type cylinder device having a structure that does not require a gear-shaped component in the suction / exhaust mechanism part (Japanese Patent Laid-Open No. 56-118501 and Japanese Utility Model Laid-Open No. 57-8718).
4 and Japanese Utility Model Laid-Open No. 58-92486).

As shown in FIGS. 70 and 71, a rotary cylinder device disclosed in Japanese Patent Laid-Open No. 56-118501 discloses a circular cylinder member 102 fixed in a casing 101 by press fitting, and the cylinder member 102. Member 10
2 and a support member 104 that rotates in a circular cavity 103 formed in the central portion of the second. Cylinder member 10
In FIG. 2, six cylinder chambers 105 arranged radially are provided.
a, 105b, 105c, 105d, 105e, 105
f is formed and communicated with the central cavity 103, respectively. Each of these cylinder chambers 105a to 105f
The casing 101 along with the rotation of the support member 104.
Is provided so as to sequentially communicate with the suction port 106 that communicates with the outside of the cylinder to take the fluid into the cylinder device and the discharge port 107 that pressurizes the taken-in fluid and discharges the fluid.

The supporting member 104 is a disk-shaped member fixed to one end of a shaft 108 rotatably supported in a hole 101a formed in the casing 101, and a crescent-shaped valve on the surface opposite to the shaft 108. A seat 109 is attached. The valve seat 109 has an inner wall portion 103 a of the cylinder member 102.
It is arranged so as to be able to rotate in a state in which it is in close contact with a region corresponding to about a half of the circumference, and is provided so as to selectively communicate the hollow portion 103 and an arbitrary cylinder chamber. The support member 104 is provided with a hole 104a for communicating with the discharge port 107.

At the eccentric position of the support member 104, the shaft 1
10 is fixed, and the rotary piston member 11 is attached to the shaft 110.
1 is rotatably supported. The shaft 110 has a valve seat 10
Both ends are fixed to a disk-shaped support member 104 and an auxiliary plate member 113 which are arranged so as to face each other with 9 in between.
The auxiliary plate member 113 is provided with a hole 113a for communicating with the suction port 106. This auxiliary plate member 113
Rotate integrally with the support member 104. The rotary piston member 111 includes a rotation center portion 112a and a piston 11 radially extending from the rotation center portion 112a in three directions.
1a, 111b, 111c. The rotary piston member 111 revolves around the axis o1 of the cylinder member 102 as the support member 104 rotates.

With the rotation of the support member 104, the pistons 111a, 111b, 111c move from FIG.
As shown in FIG. 71D, the arrow A1 is centered around the shaft 110.
While rotating (rotating) in the direction of arrow B1 about the axis o1
By rotating (revolving) in the direction, the three pistons 111a to 111c sequentially move in and out of the fixed cylinder chambers 105a to 105f, and the outside air is sequentially taken into the cylinder chambers 105a to 105f from the suction port 106. Then, the pump operation of discharging from the discharge port 107 to the outside is repeated. According to this apparatus, the manufacturing process is easy because no advanced tooth profile processing technology is required.

[0008]

However, each of the pistons 111a to 111c rolls while rolling in the cylinder chamber 1.
05a to 105f, in order to make the movement smooth and easy, the tip portion is sharpened and the widthwise dimension when entering each cylinder chamber 105a to 105f has a margin. Inevitably, the pistons 111a to 111c and the cylinder chamber 105a are correspondingly increased.
A gap will be formed between the first and the second through 105f. As a result, there is a problem that the fluid easily leaks from the gap portion and the pump efficiency is reduced accordingly.

Further, the rotary type cylinder devices disclosed in Japanese Utility Model Laid-Open Nos. 57-87184 and 58-92486 are basically arranged, that is, radially arranged while rotating pistons arranged radially. The rotary cylinder device is the same as the rotary cylinder device described in the above-mentioned Japanese Patent Laid-Open No. 56-118501, except that the cylinder member 102 rotates. The configuration is different because the piston member 111 rotates due to rotation, the valve seat 109 is fixed to the case and does not rotate, and the rotation fulcrum of the rotating piston member 111 does not rotate.

Therefore, in the case of the type in which this cylinder chamber rotates together with the rotary piston member, unlike the above-mentioned type in which the cylinder chamber is fixed, the shape of the piston has an outer diameter almost equal to the width of the cylinder chamber. It is formed into a substantially circular disc. This is because the cylinder member also rotates in the same direction as the rotary piston member, so that when the piston moves in and out of the cylinder chamber, smooth operation can be performed even if there is almost no gap between the piston and the cylinder chamber. However, in this type, since the contact surface between the piston and the cylinder chamber is composed of the outer peripheral surface of the circular disk-shaped piston and the inner wall of the linear cylinder chamber, the area of the contact surface is small. Since this portion cannot withstand the pressure of the fluid and the fluid leaks, there remains a problem that the pump efficiency decreases when the pressure increases.

An object of the present invention is to prevent fluid from leaking from a contact portion between a piston and a cylinder member and, as a result, to convert rotary energy into rotary motion or rotary motion into fluid energy with low loss. To provide a cylinder device.

[0012]

In order to achieve the above object, a rotary cylinder device according to a first aspect of the present invention is a rotary cylinder member in which a cylinder chamber is formed so as to pass through a rotation axis and which rotates about the rotation axis. A piston that reciprocates linearly in surface contact with the cylinder chamber; a piston holding member that holds the piston and rotates about a center of rotation that is eccentric from the rotation axis of the rotating cylinder member; a rotating cylinder member and a piston holding member; Is rotatably supported and has a casing having at least one fluid inlet and at least one fluid outlet, and the piston is at a position at a certain distance from the center of rotation of the piston holding member, and with that position as the center. It is rotatably held.

Therefore, when rotation is externally input to the rotary cylinder member or piston holding member, or when pressure is applied to the piston in the cylinder chamber by introducing a fluid having a pressure from the fluid inlet, the rotary cylinder member The piston reciprocates in the cylinder chamber by rotating (revolving) about the rotation center of the piston holding member while rotating about the rotation center of the piston by the rotation of the piston holding member or the movement of the piston itself. To do.

At this time, the rotating cylinder member and the piston holding member can rotate while being respectively supported by the casing, and the piston can also rotate by itself, so that the piston rotates around the rotation center. It is possible to make a linear movement in the cylinder chamber while changing the position. As a result, even when the piston is configured to be in surface contact with the cylinder chamber, each member can smoothly rotate. For example, even if the piston has a block shape, each member can smoothly rotate. For this reason, the piston is easy to make,
The accuracy of the piston is easy to obtain. Here, the ratio of the rotation speed of the rotary cylinder member, the rotation speed of the piston holding member, and the reciprocating speed of the piston in the cylinder, that is, the rotation speed of the piston with respect to the piston holding shaft may be set to 1: 2: 1. preferable. In this case, the respective members reliably rotate without difficulty, and vibration and noise during rotation are reduced.

Further, the contact area between the piston and the cylinder chamber can be made large, and the fluid resistance at the contact surface is large as compared with the conventional one in which the contact surface is formed by so-called line contact, and the airtightness / liquid tightness is high. The tightness is enhanced, and the fluid can be prevented from leaking from the contact surface portion. Therefore, it becomes possible to convert fluid energy into rotational movement or rotational movement into fluid energy with low loss.

Moreover, since the piston reciprocates linearly in the cylinder chamber, the piston operation is smooth and stable, and vibration and noise during rotation are reduced.
In addition, since it is possible to widen the allowable range of component accuracy, it becomes easier to process parts, and conversely, if the level of component accuracy is the same as the conventional level, airtightness and reliability will be improved. Alternatively, when a fluid motor is used, it is easy to improve the performance.

Further, in the rotary cylinder device of the present invention, if the rotary shaft center of the rotary cylinder member is a drive shaft for introducing rotation from the outside, by rotating the rotary cylinder member, the piston and the piston holding member are rotated. Can be driven. By doing so, it can be used as a compressor that sucks in and compresses and discharges gas, or as a pump that sucks and discharges liquid. Moreover, the so-called center drive specification can be achieved, and when the drive shaft and the motor shaft are directly connected in the coaxial direction, the product can be well received, and it is also advantageous in terms of vibration and installation.

For example, in the case of being constituted as a rotary compressor, the rotary cylinder member and the piston holding member are relatively rotated by the rotary drive source to move the piston and discharge the fluid sucked from the fluid inlet from the outlet. At this time, the fluid inlet is formed so as to start from a position slightly inward of the position where the piston moves to the outermost circumference with the rotation of the rotary cylinder member and reach a position where the piston moves to the vicinity of the cavity, while the outlet Is preferably slightly provided at a position slightly before the position where the piston has moved to the outermost periphery as the rotary cylinder member rotates. in addition,
It is preferable to provide a check valve at the outlet that is the discharge port. In this case, since each cylinder chamber sequentially faces the outlet due to the rotation of the rotating cylinder member, even if the pressure of the fluid discharged from the outlet pulsates, the check valve works to prevent the reverse flow of the fluid when the pressure drops. can do. Further, it is preferable that the input shaft for relatively rotating the rotary cylinder member and the piston holding member be connected to the rotary cylinder member or the piston holding member via a Keret plate. In this case, for example, even if the center of the input shaft and the center of the rotating cylinder member are deviated when the rotation of the input shaft is transmitted to the rotating cylinder member, this deviation is absorbed between the cylinder member and the Kelet plate to rotate. Transmit power. Similarly, even if the center of the input shaft deviates from the center of the piston holding member when the rotation of the input shaft is transmitted to the piston holding member, the Keray plate can absorb the deviation and transmit the rotational force. .

Further, when the rotating cylinder member and the piston holding member are rotated by introducing the pressure fluid into the cylinder chamber and moving the piston by the pressure of the fluid, at least one of the rotating cylinder member and the piston holding member rotates about the output shaft. Can be taken out as a fluid rotating machine. In the case of a fluid rotating machine, the fluid inlet is opened so that the piston communicates with the cylinder chamber at a substantially outer peripheral position of the rotating cylinder member as the rotating cylinder member rotates as viewed from the rotation axis of the rotating cylinder member, It is formed so as to close the cylinder chamber at a position where the fluid does not pass directly from the inlet to the outlet in the cylinder chamber of the rotating cylinder member that is not involved in the piston, and the outlet rotates when viewed from the rotation axis of the rotating cylinder member. Accordingly, the piston is formed so as to open in the cylinder chamber of the rotary cylinder member on the side not involved in the piston so that the fluid does not directly pass from the inlet to the outlet, and to close the cylinder chamber at the substantially outer peripheral position of the rotary cylinder member. Is preferred. When the rotary cylinder device is configured as a rotary compressor, the fluid inlet has a piston in the cylinder chamber at a substantially outer peripheral position of the rotary cylinder member as the rotary cylinder member rotates as viewed from the rotation axis of the rotary cylinder member. Is formed so as to communicate with each other, and is formed so as to close with the cylinder chamber at a substantially central position of the rotary cylinder member, and the outlet is configured such that when the rotary cylinder member rotates, the piston causes the piston of the rotary cylinder member to rotate. It is preferable that the cylinder chamber is opened so as to communicate with the cylinder chamber at a position advanced from the substantially central position to the outer peripheral side, and is closed at the substantially outer peripheral position of the rotary cylinder member.

Further, when the fluid rotating machine is constructed, it is preferable to provide a lubricant circulating mechanism. In this case, by lubricating the sliding surfaces of the piston, the piston holding member, the rotating cylinder member, etc., it is possible to rotate at a higher speed.

Further, a fluid power generator may be constructed by connecting a power generation mechanism to the output side of the above fluid rotating machine. In this case, power generation can be performed using the fluid rotating machine described above.

According to a second aspect of the present invention, in the rotary type cylinder device, a guide portion for guiding the piston in the sliding direction is formed in the cylinder chamber, and a guide engaging portion for engaging the guide portion is formed in the piston. ing. Therefore, the reciprocating linear movement of the piston becomes smooth as the guide engaging portion is guided by the guide portion.

Further, in the rotary cylinder device according to the third aspect of the invention, the fluid inlet is provided in the casing in one of the regions divided by the line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. It is provided so as to communicate with the cylinder chamber, and the outlet is provided so as to communicate with the cylinder chamber in the casing in one of the other regions divided by the line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. It is something that is done. In this case, the inlet and the outlet can be arranged far apart from each other, and even if the pressure difference between the fluid on the inlet side and the fluid on the outlet side is large, this fluid does not pass through the cylinder chamber and flows from the inlet. exit,
Alternatively, direct flow from the outlet to the inlet can be prevented. Particularly, it is preferable that the inlet and the outlet of the fluid are provided at positions facing the outer peripheral surface side of the rotating cylinder member of the casing. By doing so, it is possible to configure the cylinder chambers and the inlets and outlets so that the cylinder chambers communicate with the outer peripheral surface of the rotary cylinder member, thereby improving the cohesion of the product.

In the rotary cylinder device according to the fourth aspect, it is preferable that the surface of the piston facing the piston holding member is a flat surface. In this case, the movement of the piston becomes smooth with respect to the piston holding member. Further, it is possible to prevent a gap from being generated between the piston and the piston holding member, and prevent fluid leakage.

In the rotary cylinder device according to the fifth aspect of the present invention, it is preferable that the cross-sectional shape of the piston and the cross-sectional shape of the cylinder chamber have similar shapes so as to form a slight slidable gap. In this case, it is possible to prevent a gap from being generated between the rotary cylinder member and the piston, and prevent fluid leakage. Here, the shape of the piston does not have to be a special shape as long as it matches the cross-sectional shape of the cylinder chamber. For example, even if the piston has a block shape whose entire surface is formed into a flat surface, each member smoothly rotates. It becomes possible. As a result, the piston is easily manufactured, and the accuracy of the piston is easily obtained. In addition, at least one side surface of both flat side surfaces of the cylinder chamber, preferably both side surfaces,
Most preferably, the side surface of the piston may be provided with a flat surface that makes surface contact with the entire four surfaces including the surface formed by the piston holding member and the casing. Further, the cross-sectional shape of the piston is not limited to the rectangular shape, but may be a different shape, and the cross-sectional shape of the cylinder chamber may be made to match the piston shape. In this case, since it is not necessary to form both side walls of the cylinder chamber in which the piston slides perpendicularly to the bottom surface, the cylinder chamber can be easily processed. For example, if both corners of the bottom surface of the piston are rounded, the corners of the cylinder chamber in which the piston slides can be rounded, which makes the machining of the cylinder chamber even easier.

According to a sixth aspect of the present invention, in the rotary type cylinder device, a magnetic fluid is arranged in a gap formed between the piston and the cylinder chamber, and a magnet for holding the magnetic fluid in the gap is provided in the piston and the cylinder chamber. It is also possible to provide in the vicinity of the contact area with. In this case, the magnetic fluid held by the magnet is filled in the gap between the piston and the rotating cylinder member. Therefore, the slight gap between the portion where the piston and the cylinder member face each other is more surely sealed,
It is possible to more reliably prevent the fluid from leaking from the contact portion.

Further, in the rotary type cylinder device according to a seventh aspect of the present invention, a plurality of pistons and cylinder chambers are formed, and the plurality of cylinder chambers are formed so as to pass through and cross the rotation axis of the rotary cylinder member. Is preferred. In this case, a rotary cylinder device that is rotated by a plurality of pistons is provided.

Further, in the rotary type cylinder device according to the present invention, the cylinder chambers are arranged at positions equidistantly distributed in the circumferential direction in the rotary cylinder member. Therefore, the rotational balance of the rotary cylinder member is improved, vibration and noise can be prevented, and a rotary cylinder device suitable for high-speed rotation is provided.

Further, in the rotary type cylinder device according to the ninth aspect, the length in the moving direction of the piston at the portion where the plurality of cylinder chambers intersect is shorter than the length of the piston. Therefore, the piston that performs the reciprocating linear motion crosses the other cylinder chamber that intersects while being guided by the wall surface of the cylinder chamber that is moving when passing the portion where the cylinder chambers intersect, so that it does not hit the other cylinder chambers. You can pass smoothly.

Further, in the rotary type cylinder device according to the tenth aspect, it is preferable that the chamfered portion is formed at a portion where the plurality of cylinder chambers intersect. Also in this case, the passage of the portion where the cylinder chambers of the piston intersect becomes smoother.

In the rotary type cylinder device of the present invention, it is preferable to provide back pressure relief means for reducing the back pressure, which is a resistance against the relative rotation between the rotary cylinder member and the piston holding member, on these sliding contact surfaces. In this case, the piston operates to rotate the rotating cylinder member and the piston holding member, which causes back pressure that prevents these movements.However, since the back pressure relief means reduces this back pressure, the rotating cylinder member and the piston holding member are retained. It is possible to smooth the movement of the members and the like. For example, the back pressure relief means may be a piston back-and-forth dynamic back pressure relief means for releasing the back pressure acting in the moving direction of the piston, and a cylinder for releasing the back pressure generated between the rotating cylinder member and the casing. It may be a side back pressure relief means, or may be a piston holding member side back pressure relief means for releasing back pressure generated between the piston holding member and the casing. Also, all of these may be provided.

Further, in the rotary type cylinder device of the present invention, it is preferable that the rotary cylinder member and the piston holding member are rotatably supported by a bearing member which simultaneously receives a thrust load and a radial load. In this case, the structure of the portion that rotatably supports the rotary cylinder member and the piston holding member becomes simple, and the size and cost of the device can be reduced.

In the rotary cylinder device of the present invention, the rotary cylinder member may be rotatably supported by the bearing plate, and the bearing plate may be adjustable by the push adjusting screw and the pull adjusting screw. In this case, the inclination of the bearing plate that supports the rotary cylinder member can be adjusted by changing the screwing amounts of the push screw and the pull screw. Therefore, the accuracy of parts of the rotary cylinder member in the thrust direction can be reduced.

In the rotary cylinder device of the present invention, the piston holding member may be rotatably supported by the bearing plate, and the bearing plate may be adjustable by the push adjusting screw and the pull adjusting screw. In this case, the inclination of the bearing plate that supports the piston holding member can be adjusted by changing the screwing amounts of the push screw and the pull screw. Therefore, the accuracy of the piston holding member in the thrust direction can be reduced.

[0035]

BEST MODE FOR CARRYING OUT THE INVENTION The structure of the present invention will be described below in detail based on the best mode shown in the drawings.

An embodiment of the rotary cylinder device of the present invention will be described with reference to FIGS. In each of the embodiments, a rotary pump device that delivers gas in a fixed direction is described, but the medium to be delivered is not limited to gas, but can be any fluid including liquid. Further, the present invention is not limited to the pump device, and is also suitable for various devices configured by utilizing the rotating operation of the rotary cylinder member, such as an air compressor and an air motor.

As shown in FIGS. 1 and 2, the rotary cylinder device 1 has a plurality of radially arranged cylinder chambers 22 and 23, and a rotary cylinder member 2 which rotates about a rotation axis O. Pistons 3 and 4 that make linear reciprocating motion by making surface contact in the cylinder chambers 22 and 23, and pistons 3 and 4
And a piston holding member 5 that is eccentric from the rotation cylinder member 2 and rotates around the rotation center X, and rotatably supports the rotation cylinder member 2 and the piston holding member 5 and at least one fluid inlet 61 and at least one. Mainly composed of a casing 6 having two fluid outlets 62, the pistons 3 and 4 are held rotatably about shaft centers X1 and X2 which are located at a certain distance from the center of rotation of the piston holding member 5. Has been done. More specifically, the rotary cylinder member 2 having a circular shape and the pistons 3 and 4 at two eccentric rotation center positions X1 and X2 separated by 180 degrees, respectively.
A rotatably holding piston and a rotatably rotating piston having a piston holding member 5 that rotates about a position eccentric from the rotation axis O of the rotating cylinder member 2 as a rotation center position X, and both rotating members of the rotating cylinder member 2 and the piston holding member 5. It has a casing 6 that supports it rotatably. Although the rotary cylinder member 2 employs the cylinder chambers 22 and 23 and the pistons 3 and 4 in the present embodiment, the invention is not limited to this, and at least 1
It only needs to have two cylinder chambers and a piston.

As shown in FIGS. 1, 2 and 3, the rotary cylinder member 2 is formed in a circular shape having a predetermined thickness and is rotatably arranged in the internal space of the casing 6. One end of the support shaft 21 is press-fitted into and fixed to a recess that surrounds the rotation axis O of the one end surface of the rotary cylinder member 2, that is, the lower end surface in FIGS. 1 and 3. The other end of the support shaft 21 is provided with two bearing members 7a arranged in the casing 6 and stacked in the axial direction.
It is rotatably supported by 7b. Therefore, the rotary cylinder member 2 has the casing 6 with the support shaft 21 as the center of rotation.
It can be rotated inside.

On the other end surface of the rotary cylinder member 2, that is, on the upper end surface in FIGS. 1 and 3, there is provided a space formed by a cross-shaped groove formed by using four fan-shaped base portions 25. . This cross-shaped space is composed of four cylinder portions 22a, 22b, 23a, 23b and a portion 24 (hereinafter referred to as a hollow portion) where these intersect.
That is, on the other end surface of the rotary cylinder member 2, there is formed a cavity portion 24 having a predetermined area centered on the rotation axis O and having a bottom surface. And this cavity 24
Four cylinder portions 22a, 22b, 23a, 23b having a rectangular cross section are provided radially about the inner rotation axis O. Cylinder parts 22a, 22b, 23a, 2
The upper surface of 3b is open, and the other three surfaces are all flat. Then, the first cylinder portion 22
a, the hollow portion 24, and the second cylinder portion 22b form the cylinder chamber 22, and the third cylinder portion 23a and the hollow portion 2
4, the cylinder chamber 23 by the fourth cylinder portion 23b
Are formed respectively. As is clear from FIG. 2 and the like, the cylinder chambers 22 and 23 are formed so as to intersect with each other, including the rotation axis O of the rotary cylinder member 2, and are arranged at positions equally distributed in the circumferential direction. There is. In this specification, “upper” and “lower” are used for convenience of description,
This word is used for convenience based on the drawings, and does not mean “above” or “below” in an absolute sense.

Incidentally, these first to fourth cylinder parts 2
Pistons 3 and 4 held by a piston holding member 5 are slidably fitted into 2a to 23b. The facing surfaces of the cylinder parts 22a to 23b facing the pistons 3 and 4 and the surfaces facing the pistons 3 and 4 are:
The flat surfaces are formed so that they are in contact with each other. Since the contact surfaces of the pistons 3 and 4 and the cylinder portions 22a to 23b are flat surfaces as described above, the contact area is large and the airtightness of the fluid at the contact portions is high. Therefore, it is possible to make it difficult for the fluid to leak through the gaps between the pistons 3 and 4 and the cylinder parts 22a to 23b.

The cylinder chambers 22 and 23 formed as described above penetrate the rotary cylinder member 2 in the radial direction and are open at the outer peripheral surface 2a thereof. Therefore, each of the cylinder chambers 22 and 23 can communicate with a suction port (fluid inlet) 61 and a discharge port (fluid outlet) 62 formed in the casing 6.

By the rotation of the piston holding member 5,
When the rotary cylinder member 2 and the piston holding member 5 rotate, the pistons 3 and 4 apparently make linear reciprocating linear motions in the cylinder chambers 22 and 23. The length in the moving direction of the pistons 3 and 4 of the cavity 24, which is the portion where the cylinder chambers 22 and 23 intersect, is determined by the contact surface of the pistons 3 and 4 (the surface facing both side wall surfaces of the cylinder chambers 22 and 23). ) Is shorter than the length.

The cavity 24 and the first to fourth cylinder portions 22a to 23b radially arranged around the cavity 24 are provided.
Two thin guide grooves 26a and 27a are formed in a cross shape on the bottom surface of the. On the other hand, the bottom portions of the pistons 3 and 4 are provided with convex pieces 3b and 4b which are guide engaging portions to be fitted into the above-mentioned guide grooves 26a and 27a. The convex pieces 3b, 4b engage with the guide grooves 26a, 27a to form a linear motion guide. Therefore, the pistons 3 and 4 are stably reciprocated linearly along the two guide grooves 26a and 27a between the pair of cylinder portions 22a and 22b or between the pair of cylinder portions 22a and 23b.

On the other hand, the piston holding member 5 is formed in a circular shape having an outer diameter smaller than the outer diameter of the rotary cylinder member 2. At the rotation center position X of the piston holding member 5, one end of the support shaft 51 is inserted and fixed by press fitting. The rotation center position X of the piston holding member 5
Is provided at a position eccentric from the rotational axis O of the rotary cylinder member 2 described above. The other end of the support shaft 51 has bearing members 8a, 8b arranged in the casing 6.
Is rotatably supported on the casing 6, and the tip side thereof projects to the outside of the casing 6. Then, by connecting the protruding portion to an output shaft (not shown) of a drive source such as a motor, the piston holding member 5 is rotated about the support shaft 51 by the driving force of the drive source such as a motor, and the rotary cylinder member 2 is rotated. Is rotatably driven at the eccentric position.

A support shaft 52 for holding the piston 3 rotatably and a support shaft 53 for holding the piston 4 rotatably are provided on the surface of the piston holding member 5 opposite to the surface on which the support shaft 51 is fixed. It is fixed upright. The support shaft 52,
Pistons 3 and 4 are rotatably fitted in 53.

The pistons 3 and 4 are formed such that the front and rear surfaces 31, 31, 41, 41 at the time of reciprocating linear motion are slightly rounded, but the other four surfaces, that is, in the cylinder chambers 22, 23. The upper surface 32 in the fitted state,
42, bottom surfaces 33, 43 and both side surfaces 34, 34, 44, 4
4 is formed in a plane. That is, the pistons 3, 4
Has a substantially rectangular block shape. The upper surface 3 of the surfaces formed on the flat surfaces of the pistons 3 and 4
Bottom surfaces 33, 43 excluding 2, 42 and both side surfaces 34, 34, 4
Reference numerals 4 and 44 serve as contact surfaces with the cylinder chambers 22 and 23 when fitted into the cylinder chambers 22 and 23. In addition, bottomed holes 3a and 4a for rotatably fitting the support shafts 52 and 53 are provided at the central portions of the pistons 3 and 4. The holes 3a and 4a may be through holes as long as the support shafts 52 and 53 do not abut the guide grooves 26a and 27a.

The piston holding member 5 and the piston 3,
FIG. 15 shows the relationship with the locus of the rotation No. 4 during rotation. The radius R1 of the piston holding member 5 and 1 / the distance between the support shafts 52, 53
The relationship between the distance R2 of 2 and the radius R3 of the outermost diameter locus during rotation of the pistons 3 and 4 is R1> (R2 + R3), and a radius difference ΔR occurs. When the radius R1 is smaller than the distance R2 + the radius R3, the piston outermost diameter locus jumps out from the piston holding member 5 during operation, and in order to secure the rotation stability and the hermeticity of the pistons 3 and 4. It is necessary to improve the processing accuracy of parts. In contrast,
By setting the relationship of radius R1> distance R2 + radius R3 as described above, it becomes easy to secure the rotation stability and the hermeticity of the pistons 3 and 4 without making the machining accuracy of the parts so severe. However, this relationship is for ensuring the hermeticity, etc., and is not limited to this relationship.
It goes without saying that the radius R1 may be substantially equal to or smaller than the distance R2 + the radius R3.

The casing 6 is composed of two case halves, that is, an upper case 63 for rotatably supporting the piston holding member 5 and a lower case 64 for rotatably supporting the rotary cylinder member 2. ing. The upper case 63 and the lower case 64 form a casing 6 that forms a sealed internal space by fixing the fitting protrusions (anchor parts) 63a, 64a with each other by screws or the like. It has become a thing. As described above, the fitting protrusions 63a and 64a are fitted to each other by the brazing structure, so that the upper case 63 and the lower case 64 can be accurately positioned and centered, and the deviation can be prevented. .

The upper case 63 has a protrusion 63a for fitting when it is attached to the lower case 64, and has a large circular space 63 for rotatably storing the piston holding member 5.
b, and two bearing members 8a, 8b that rotatably support the support shaft 51 fixed to the rotation center of the piston holding member 5.
And a circular small space 63c for press-fitting and fixing the same as the inner space.

The fitting projection 63a is formed in a circular shape along the outer edge of the large circular space 63b, and projects toward the lower case 64 side. The protrusion height of the fitting protrusion 63a is slightly lower than the protrusion height of the fitting protrusion 64a formed on the lower case 64, and the radius thereof is slightly larger than the radius of the fitting protrusion 64a. Has been done. As a result, the fitting protrusion 63a of the upper case 63 becomes
The fitting protrusions 64a are fitted to each other so as to cover the outer sides of the fitting protrusions 64a.

Then, a small space 63c of the upper case 63
An insertion hole 63d for inserting the support shaft 51 is provided on the bottom surface of the. The one end side of the support shaft 51 has the insertion hole 63.
It projects from the d to the outside of the casing 6.

On the other hand, the lower case 64 is provided with a fitting projection 64a for attachment to the upper case 63, and has a large circular space 64b for rotatably storing the rotary cylinder member 2 and the rotary cylinder member 2. Two bearing members 7 that rotatably support the support shaft 21 fixed to the rotation axis O.
Small circular space 64c for press-fitting and fixing a and 7b
It has a cup shape having and as an internal space.

The fitting protrusion 64a is formed in a circular shape along the outer edge of the large circular space 64b, and projects toward the upper case 63 side. The protrusion height of the fitting protrusion 64a is slightly higher than the protrusion height of the fitting protrusion 63a formed on the upper case 63, and its radius is slightly smaller than the radius of the fitting protrusion 63a. Has been done.

In the large space 64b of the lower case 64 thus formed, the rotary cylinder member 2 is rotatably arranged. With the rotary cylinder member 2 arranged, a suction port 61 for sucking an external fluid into the casing 6 is provided at a position facing the outer peripheral surface 2a of the rotary cylinder member 2, that is, at the inner wall 64d of the large space 64b.
And a discharge port 62 for discharging the fluid sucked into the casing 6 to the outside.

The suction port 61 is the inner wall 6 of the large space 64b.
4d formed over a range of an angle of about 80 degrees, a shallow recess 61a, a communication hole 61b for communicating the recess 61a with the outside of the casing 6, and an intake pipe connected to the outer surface side of the casing 6 of the communication hole 61b. 61c. Then, the recess 61a is formed in the rotary cylinder member 2
When is rotated, the cylinder portions 22a to 23b are connected to each other.

Further, the discharge port 62 is the recess 6 of the suction port 61.
1a, a shallow recess 62a formed at a position of about 10 degrees and extending to about 80 degrees, a communication hole 62b for communicating the recess 62a with the outside of the casing 6, and an outer surface of the casing 6 of the communication hole 62b. And an exhaust pipe 62c connected to the side. And the recess 62a is
When the rotary cylinder member 2 rotates, each cylinder part 22
a to 23b are connected to each other.

In the rotary type cylinder device 1 constructed as described above, when the piston holding member 5 makes a rotational movement at a constant angular velocity by driving a motor or the like, the pistons 3 and 4 have a constant angular velocity about the rotation center position X. It makes a rotary motion, and the rotary cylinder member 2 also makes a uniform angular velocity motion in accordance with this motion.
By this operation, the pump operation is performed.

Next, the operation of the rotary cylinder device 1 according to the first embodiment of the present invention will be described with reference to FIGS. The guide grooves 26a and 27a forming part of the guide means of the pistons 3 and 4 are not shown.

In FIG. 4, the piston 3 that reciprocates in the cylinder chamber 22 is located in the hollow portion 24 of the rotary cylinder member 2. One end is at the inlet of the cylinder portion 22a and the other end is at the inlet of the cylinder portion 22b. Each is in a state of slightly entering. That is, the piston 3 is in a state where both side surfaces 34, 34 and the bottom surface 33 formed in a plane are in contact with both inner walls and bottom surfaces of the cylinder portions 22a, 22b and a bottom surface of the cavity portion 24 which are also formed in a plane. Has become. In such an intermediate position, the piston 3
The cylinder portions 22a and 22b on both sides of the cavity portion 24 are fitted at the same time.
Both a and 22b are filled with the fluid taken in through the suction port 61.

In the state shown in FIG. 4, the cylinder portion 22
The outermost peripheral end of a is in a state where it slightly starts to communicate with the recess 62a of the discharge port 62, and the cylinder portion 22a
Is in a state of communicating with the exhaust pipe 62c through the recess 62a. Further, the outermost peripheral end portion of the cylinder portion 22b is in a state immediately before the communication state with the recess 61a of the suction port 61 is finished, and the cylinder portion 22b has the recess 6a.
It is in a state of communicating with the intake pipe 61c via 1a. As described above, since the piston 3 is in the state of approaching the hollow portion 24, all the cylinder parts 22a to 23b are divided and closed by the piston 3.

On the other hand, the piston 4 that reciprocates in the cylinder parts 23a and 23b is in a state where it has advanced to the outermost peripheral end of the cylinder part 23b of the rotary cylinder member 2. That is, the piston 4 is in the state of being located at one end of the reciprocating groove, and the both side surfaces 4 formed on the plane are
4, 44 and the bottom surface 43 are in a state of being simultaneously engaged with both inner walls and the bottom surface of the cylinder portion 23b which is also formed by a flat surface.

Then, the piston 4 of the cylinder portion 23b
The space surrounded by the piston 3 is filled with the fluid. In addition, the cylinder portion 23a is connected to the other cylinder portions 22a, 22b, 23b by the piston 3.
It is isolated from the cylinder part 2
The inside of 3a is also filled with the fluid. At this time, the outermost peripheral end of the cylinder portion 23b is in a state of facing the position between the recess 61a of the suction port 61 and the recess 62a of the discharge port 62.

When the piston holding member 5 is rotated clockwise (direction indicated by arrow A) from the state shown in FIG. 4 by the motor driving or the like, the pistons 3 and 4 move in the direction indicated by arrow A together with the support shafts 52 and 53. To do. By the operation of the pistons 3 and 4 at this time, a rotational force in the direction of arrow B (clockwise) is applied to the rotary cylinder member 2, and the rotary cylinder 2 moves in the direction of arrow B.
Rotate in the direction. By the relative rotation of the pistons 3 and 4 and the rotary cylinder member 2 as described above, the respective pistons 3 and 4 are
Reciprocates in the cylinder chambers 22 and 23.

The orbital rotational movement of the pistons 3, 4 at this time, that is, the rotational movement of the piston holding member 5 around the rotational center position X is the rotational speed about the rotational axis O of the rotary cylinder member 2. The rotational movement is twice as fast. This means that the radii of rotation of the pistons 3 and 4 are 1/2 of the radius of gyration of the rotary cylinder member 2 (cylinder reference circle), and the rotary motion of the pistons 3 and 4 is the rotary motion of the rotary cylinder member 2. This is because it is a circular cycloid movement. The rotations of the pistons 3 and 4, that is, the rotations about the support shafts 52 and 53, respectively, are the same angular velocity motions as the rotating cylinder member 2. Therefore, the number of rotations of the rotary cylinder member 2 versus the piston holding member 5
The ratio of the number of revolutions to the number of revolutions of the pistons 3 and 4 with respect to the support shafts 52 and 53 is 1: 2: 1.

The cylinder reference circle is as shown in FIG.
From the rotation axis O of the rotary cylinder member 2, the rotation center position X2
A circle whose radius is the length to the center of.

Further, due to this rotation operation, the pistons 3 and 4 in the cylinder chambers 22 and 23 move to the rotary cylinder member 2
The piston 3 apparently reciprocates linearly between the pair of cylinder portions 22a and 22b, and the piston 4 apparently reciprocates linearly between the pair of cylinder portions 23a and 23b while applying a rotational force. The pistons 3 and 4 have a rotary cylinder member 2 of 1
While rotating, between the cylinder parts 22a and 22b and 23
It makes one round trip between a and 23b, and the number of reciprocating movements of the pistons 3, 4 and the number of revolutions of the rotary cylinder member 2 have a 1: 1 relationship.

From the state shown in FIG.
FIG. 5 shows a state in which the cylinder member 2 is rotated by 30 degrees and the cylinder member 2 is rotated by 30 degrees.

That is, by the above-described operation from FIG. 4 to FIG. 5, the piston 3 advances from the state of traversing the hollow portion 24 to the inside of the cylinder portion 22a by about 1/2.
During this movement, the piston 3 and the cylinder part 22a are
Since the flat surfaces face each other, there is almost no leakage of fluid from the contact surfaces. By this operation, the fluid in the cylinder portion 22a is efficiently discharged to the discharge pipe 62c through the recess 62a. The cylinder chamber 22
Since the distance in the longitudinal direction of a is shorter than twice the total length of the piston 3, it has advanced about 1/2, but the rear end portion of the piston 3 still remains in the cavity 24. It is in a state of being.

On the other hand, by the movement of the piston 3 in the direction of the cylinder portion 22a, the cylinder portions 22b, 23a and the cylinder portion 23b sealed by the piston 3 become a series of spaces. The fluid flowing from the suction port 61 into the cylinder portions 22b, 23a, 23b is filled in the series of spaces.

Further, by the operation during this period, the piston 4 moves from the innermost portion of the cylinder portion 23b to the cavity portion 24 side by about 1 /.
Move about 9. At the time of this movement, the piston 4 and the cylinder portion 23b are in contact with each other on their flat surfaces, so that there is almost no leakage of fluid from between the contact surfaces (sliding surfaces). By this operation, the external fluid efficiently flows into the cylinder portion 23b from the recess 61a via the intake pipe 61c. At this point, the piston 4 is completely in the cylinder portion 23b.

FIG. 6 shows a state in which the piston holding member 5 further rotates 60 degrees from the state of FIG. 5, and thereby the cylinder member 2 further rotates 30 degrees.

That is, by the operation shown in FIGS. 5 to 6, the piston 3 is moved to the inside of the cylinder portion 22a by about 1 mm.
1/2 further from the position where it entered, specifically about 8
Move to the position where you entered / 9. By this operation,
The fluid remaining in the cylinder portion 22a is efficiently discharged to the exhaust pipe 62c through the recess 62a.

Further, by the operation during this period, the piston 4 further moves in the cylinder portion 23b toward the cavity portion 24 side. By this operation, the external fluid further flows into the cylinder portion 23b from the recess 61a via the intake pipe 61c. At this point, the front end portion of the piston 4 is
It is in a state of advancing into the hollow portion 24.

On the other hand, during this operation, the cylinder portion 22
b, 23a and a part of the cylinder part 22a are cavities 24
Through which the fluid flowing from the suction port 61 into the cylinder portions 22b and 23a is filled.

FIG. 7 shows a state in which the piston holding member 5 further rotates 60 degrees from the state shown in FIG. 6, and thereby the cylinder member 2 further rotates 30 degrees.

That is, the piston 3 is moved to the inside of the cylinder portion 22a by about 8 by the above-described operation from FIG. 6 to FIG.
It moves further from the position where it enters about / 9 to the inner side, specifically, to the outermost peripheral end of the cylinder portion 22a. By this operation, the fluid remaining in the cylinder portion 22a is efficiently discharged to the exhaust pipe 62c through the recess 62a. At this point, that is, in the state where the rotary cylinder member 2 has been rotated 90 degrees in the direction of arrow B from the initial state shown in FIG. 4, the outermost peripheral end of the cylinder portion 22a is in the recess 61a of the suction port 61 and the discharge state. The state is opposite to the position between the recesses 62a of the outlet 62, and the discharge operation has already been completed.

On the other hand, by the operation during this period, the piston 4 crosses the hollow portion 24 from the innermost side of the cylinder portion 23b, and further moves to the position where the tip portion enters the cylinder portion 23a. By the operation of the piston 4, one end of the piston 4 enters the inlet of the cylinder portion 23b and the other end of the piston 4 enters the inlet of the cylinder portion 23a at the same time. That is, the piston 4 is in an intermediate position in the reciprocating groove, and the side surfaces 44, 44 and the bottom surface 43, which are formed in a plane, have the same cylinder portions 23a, 23b formed in a plane. Both inner walls and the bottom surface and the bottom surface of the hollow portion 24 are in contact with each other at the same time.

At this time, the outermost peripheral end of the cylinder portion 23a is slightly in communication with the recess 62a of the discharge port 62, and the cylinder chamber 23a communicates with the exhaust pipe 62c through the recess 62a. It is in the state of doing. Further, the outermost peripheral end portion of the cylinder portion 23b is in a state immediately before the communication state with the recess 61a of the suction port 61 is finished, and the cylinder portion 22b is in a state where the suction operation of the fluid is almost finished. There is. As described above, since the piston 4 is in the state of approaching the hollow portion 24, the piston 4 causes the cylinder portions 22a-2
At this point, 3b is again divided and is in a closed state.

At this time, the pistons 3 and 4 are in a state in which the positions of the pistons 3 and 4 are interchanged with each other in the state shown in FIG. That is, in the pistons 3 and 4, the piston holding member 5 rotates 180 degrees, and at the same time, the rotating cylinder member 2 rotates 9 degrees.
By rotating 0 degrees, the cylinder parts 22a-23b
One of the cylinder parts moves into and out of the cylinder part, and the positions of the other are switched. Then, the rotary cylinder device 1 of the present embodiment is configured to perform the pump operation by repeating this operation. That is, the pistons 3 and 4 are the piston holding members 5
Is rotated 180 degrees, that is, 360 degrees from the initial time point, returns to the initial position shown in FIG. On the other hand, the rotary cylinder member 2 rotates 180 degrees during this period.

Therefore, the piston holding member 5 rotates twice,
When rotating 720 degrees, the rotating cylinder member 2
Makes one full rotation, 360 degrees. As a result, the pistons 3 and 4 are paired with each other in the pair of cylinder parts 22a-23.
Apparent reciprocal linear motion between b. That is, when the piston holding member 5 rotates twice, the piston 3,
4 completes a series of reciprocating operations once, and makes one rotation with respect to the support shafts 52 and 53.

During such operation, each piston 3,
4 will face each cylinder part 22a-23b by the planes with a large contact area. Therefore, the structure is such that the fluid does not leak from the gap between the surfaces that face each other and the surfaces that are actually in contact with each other. Therefore, the leakage of fluid between the spaces is prevented, and the pump can be made efficient.

In the rotary cylinder device 1 of the first embodiment described above, the number of cylinder chambers is two (4 cylinder parts) and the number of pistons is two. The number may be one. Further, the number of cylinder chambers and pistons may be three as in the second and third embodiments shown in FIGS. 8 and 9.

The rotary cylinder device 1 shown in FIG. 8 as the second embodiment of the present invention has a casing 6 as in the rotary cylinder device 1 of the first embodiment.
6 cylinder parts 22a, 22b, 23a, 23
A rotary cylinder member 2 including b, 28a, 28b and six fan-shaped bases 25 is rotatably arranged. That is,
In this embodiment, the cylinder chamber 22 is formed by the cylinder portions 22a and 22b and the hollow portion 24.
The cylinder chamber 23 is formed by 23b and the hollow portion 24, and the cylinder chamber 28 is formed by the cylinder portions 28a and 28b and the hollow portion 24. A piston holding member (not shown) is rotatably arranged at the eccentric position of the rotary cylinder member 2, and the three pistons 3, 4, 9 are rotatably held by the piston holding member. As in the rotary cylinder device 1 of the above-described embodiment, the rotation ratio of both members arranged in the casing 6 of the rotary cylinder device 1 is set with respect to the rotation number of the piston holding member being 2. The rotation speed of the cylinder member 2 is 1.

In the rotary cylinder device 1 thus constructed, when the pistons 3, 4, 9 rotate in the direction of arrow A'due to the rotation of the piston holding member, the rotary cylinder member 2 moves in the direction of the arrow as a result of this operation. It is designed to rotate in the B'direction. As a result, the piston 3 moves into the cylinder chamber 22.
The piston 4 reciprocally moves in the cylinder chamber 23 and the piston 9 reciprocally moves in the cylinder chamber 28 while traversing the cavity 24.

The longitudinal dimension of each piston 3, 4, 9 is such that it can engage with both the inner walls of the cylinder chambers on both sides of the cavity 24 when traversing the cavity 24. There is. Therefore, the pistons 3, 4, 9 simultaneously contact the cylinder chambers on both sides when traversing the cavity 24. Of course, each piston 3, 4, 9 is designed so as not to collide with the other pistons 3, 4, 9 when traversing the cavity 24. As a result, in the rotary cylinder device 1, the pistons 3, 4, 9 rotate while being constantly guided by one of the cylinder chambers, and as a result, the pistons 3, 4, 9 move in the cylinder chambers 22, 23, 28. It will surely come in and go out, and pump operation will be performed.

The rotary cylinder device 1 shown in FIG. 9 as the third embodiment of the present invention has six cylinder portions 22a in the casing 6, as in the first and second embodiments. , 22b, 23a, 23b, 28a,
The rotary cylinder member 2 provided with 28b and six fan-shaped bases 25 is rotatably arranged.
A piston holding member (not shown) is rotatably arranged at the eccentric position. The three pistons 3, 4, 9 are rotatably held by the piston holding member. As in the rotary cylinder device 1 of the embodiment shown in FIGS. 1 and 8, the rotation ratio of both members arranged in the casing 6 of the rotary cylinder device 1 is such that the rotation number of the piston holding member is 2. On the other hand, the rotation speed of the rotary cylinder member 2 and the rotation speed of the pistons 3, 4 with respect to the support shafts 52, 53 are one.

In the rotary cylinder device 1 thus constructed, when the pistons 3, 4, 9 rotate in the arrow A "direction by the rotation of the piston holding member, the rotary cylinder member 2 moves in the arrow direction in accordance with this operation. It is designed to rotate in the B "direction. As a result, the piston 3 moves into the cylinder chamber 22.
The piston 4 makes an apparent reciprocating motion while traversing the cylinder chamber 23 and the piston 9 in the cylinder chamber 28 while traversing the cavity / passage 241 respectively.

On both sides of the cavity / passage 241, guide pillars 26 having a crescent-shaped cross section are provided upright on the casing 6.
A guide column 27 having a substantially semicircular cross section is arranged, and these guide columns 26, 27 guide the pistons 3, 4, 9 passing through the inside of the cavity / passage 241. In the rotary type cylinder device 1 shown in FIG. 9, each piston 3, 4, 9 is composed of a substantially cubic block, and when it crosses the cavity / passage 241, it separates from any cylinder chamber. It will be in a state of being. Therefore, when the pistons 3, 4, 9 cross the cavity / passage 241, the guide columns 26, 27 allow the pistons 3, 4, 9 to pass while maintaining a predetermined posture. In addition to the guide columns 26 and 27, a small groove for guide is provided on the bottom surface in the cavity / passage 241 as in the first embodiment described above.
The small grooves and the guide columns 26, 27 may cooperate to guide the pistons 3, 4, 9.

The rotary cylinder device 1 of the type having the six cylinder chambers and the three pistons as shown in FIGS. 8 and 9 has a good balance between intake and exhaust and little torque fluctuation.

Further, in each of the above-described embodiments, when the pistons each having the outer surface formed into a flat surface move in and out of each of the cylinder chambers having the inner wall formed into a flat surface, the resistance force caused by the two surfaces being opposed to each other. Is designed to prevent fluid leakage between spaces, but in addition to this, a filling part with viscous grease etc. is provided on the facing part between each piston and each cylinder chamber to maintain hermeticity while maintaining lubricity. You can raise it. in this case,
A recess may be formed on both side surfaces of the piston, and the recess may be used as a filling portion. For example, as shown in FIG. 72, concave portions 3d and 4d may be formed as filling portions on both side surfaces 34 and 44 of the pistons 3 and 4, and the viscous grease or the like may be accumulated in the concave portions 3d and 4d. By forming the concave portions 3d and 4d, the piston 3,
It is also designed to soften the resistance of 4 when reciprocating.

Further, in the above-described first embodiment, the support shaft 51 of the piston holding member 5 is projected from the casing 6, and the projecting portion is connected to the drive source to rotate the piston holding member 5. Although the rotary cylinder member 2 is configured to be driven by the rotary cylinder member 1, the support shaft 21 of the rotary cylinder member 2 is protruded from the casing 6 as in the rotary cylinder device 1 shown in FIG. The portion 21a may be connected to a drive source (not shown) such as a motor so that the support shaft 21 side serves as the input side and the piston holding member 5 is driven by the rotary cylinder member 2. With this configuration, a so-called center drive type is used, and when the support shaft 21 is directly connected to the motor, the product can be stored well.

Further, in the above-described first embodiment, the recess 61a of the suction port 61 and the recess 62a of the discharge port 62 are both formed with a width of about 80 degrees.
The widths of a and 62a can be arbitrarily set according to the application. For example, when a high compression ratio is applied, for example,
When used as an air compressor, the discharge port 6
If the second recess 62a is formed to have a small volume of about 10 degrees, the compression ratio can be increased, and the fluid will be discharged from the discharge port 62 to the outside at once.

Further, in the above-described first embodiment, the suction port 61 and the discharge port 62 are provided at positions facing the outer peripheral surface of the rotary cylinder member 2 of the casing 6, respectively.
Although the suction and discharge are performed from the outside of the rotary cylinder member 2, the suction port 61 and the discharge port 62 may be provided on both sides or one side in the vertical direction of the rotary cylinder member 2.

Further, in the above-described first embodiment, the piston holding member 5 is arranged on one side of the rotary cylinder member 2, and the support shafts 52, 53 are connected from the piston holding member 5 to
Cylinder parts 22a, 22b, 2 of the rotary cylinder member 2
3a, 23b by projecting into the support shaft 5
Although the pistons 3 and 4 held by the pistons 2 and 53 are arranged in the cylinder chamber formed by the cross-shaped space of the rotary cylinder member 2, two piston holding members 90 are provided as shown in FIGS. The disk-shaped members 90a and 90b may be arranged on both sides of the rotary cylinder member 2. Hereinafter, a fourth embodiment will be described.

In the fourth embodiment, as shown in FIGS. 11 to 14, an annular bearing member 82 having a large number of needles 82a arranged at equal intervals is provided on the inner wall of the circular space in the casing 6. The rotary cylinder member 2 is rotatably supported inside thereof. The rotary cylinder member 2 is formed with a cross-shaped space in which each end is not penetrated to the outside in the radial direction and is penetrated to both sides in the axial direction. The central portion of this cross-shaped space is a hollow portion 24, and the portions radially formed from the hollow portion 24 are cylinder portions 22a, 22b, 23a, 23b. A block-shaped piston 3 having a hole 3a in the center and a block-shaped piston 4 having a hole 4a in the center are slidably fitted into the cross-shaped space formed in this manner. There is.

On both sides of the rotary cylinder member 2 in the axial direction, one end of a drive shaft 89 protruding to the outside of the casing 6 and the support shaft 9 are provided.
A piston holding member 90, which is fixed with 5 as the center of rotation, is arranged. That is, the piston holding member 90 is composed of two disk-shaped members 90a and 90b arranged with the rotary cylinder member 2 interposed therebetween, and two support shafts 52 and 53 into which the pistons 3 and 4 are inserted respectively. Are linked by. Then, when the piston holding member 90 is rotated by connecting the projecting portion of the drive shaft 89 to a drive source (not shown) such as a motor, the piston 3 causes the piston 3 to have a cylinder portion 22a, 22b and a hollow portion 24. The piston 4 slides in the chamber 22 in the cylinder chamber 23 composed of the cylinder portions 23a and 23b and the cavity 24. By this operation, the rotary cylinder member 2
Rotates in the same direction as the piston holding member 90 at a speed of 1/2, and each cylinder portion 22a, 22b, 23a, 23b
Is communicated with the suction port 61a and the discharge ports 62a, 62.

The operation of the fourth embodiment is similar to that of the first embodiment described above, and the pumping operation is performed by this operation. When the fourth embodiment is used as a pump, since the cylinder parts 22a to 23b are not in communication with the outer peripheral surface of the rotary cylinder member 2, the suction / discharge mechanism is provided on both end surfaces or one end surface of the rotary cylinder member 2. It will be provided in the outermost peripheral portion of the position where it can communicate with the cylinder parts 22a-23b.

In each of the above embodiments, one of the rotary cylinder member and the piston holding member is projected from the casing 6 as the input side and the other is incorporated in the casing 6 as the driven side. Both 21 and 51 may be projected from the casing 6, and both types may be possible with one rotary cylinder device. Furthermore, in each of the above-described embodiments, the device that rotates the cylinder member by the driving force of the motor to perform the pump activity is used. However, by feeding the fluid into the cylinder member, both the support shafts 21 and 51 are rotated. Then, a device that takes output from these support shafts 21 and 51 may be used.

Next, FIGS. 16 to 18 show an embodiment in which the rotary cylinder device of the present invention is configured as a fluid rotary machine that obtains a rotary output by using the energy of fluid. In addition,
The fluid used as the power source in this embodiment is not limited to liquid such as oil and water, but may be gas such as air and gas. Further, components having basically the same configuration and principle as those described in the embodiment shown in FIGS. 1 to 4 are designated by the same reference numerals, and the description thereof will be omitted.

In this embodiment, the shaft 21, which is the center of rotation of the rotary cylinder member 2, is used as the output shaft, and the tip end thereof is projected outside the casing 6. Further, the guide groove 26a,
The guide means composed of 27a and the convex pieces 3b and 4b is not formed between the pistons 3 and 4 and the cylinder member 2, but the movement of the piston can be performed only on the three surfaces of the cylinder chambers 22 and 23, both side walls and the bottom surface. It has a guide structure. That is, the cross-sectional shape of the groove forming the cylinder chambers 22 and 23 matches the cross-sectional shape of the pistons 3 and 4 described later in detail. In addition, one end side (center side) in the longitudinal direction of the cylinder parts 22a to 23b communicates with the hollow portion 24.

The bottom surface of the hollow portion 24 has a shape corresponding to each of the cylinder portions 22a-23b. That is, the cross-sectional shape of the cylinder parts 22a to 23b and the cross-sectional shape of the cavity portion 24 continuous to these are the same,
By processing a cross-shaped groove in a thick disk material by a method such as cutting, a cross-shaped groove composed of the hollow portion 24 and the cylinder parts 22a to 23b can be formed. Moreover, since both corners of the bottom surface of the cross groove processed by a method such as cutting may have a rounded shape, the processing is extremely easy.

Here, the pistons 3 and 4 are, for example, as shown in FIG.
As shown in (A), both corner portions 11 of the bottom surface are rounded, and the cross-sectional shape thereof is matched with the cross-sectional shape of the cylinder parts 22a-23b. The upper surfaces of the pistons 3 and 4 (the surfaces facing the piston holding member 5) are flat. Therefore, the casing 6
Also, the upper surface, both side surfaces, and the bottom surface of the pistons 3, 4 are in surface contact with the cylinder parts 22a-23b closed by the piston holding member 5 over the entire length of the pistons 3, 4 and the cylinder parts 22a- 23b and piston 3,
The airtightness and the liquidtightness between 4 are secured. That is, it is possible to more reliably prevent fluid leakage.

Then, a small space 64c of the lower case 64
An insertion hole 64 for allowing the output shaft 21 to pass therethrough is formed on the bottom surface of the
e is provided. The tip of the output shaft 21 projects to the outside of the casing 6 through the insertion hole 64e. Also,
A concave groove is provided on the inner surface of the insertion hole 64e, and the O-ring 48 is provided there.
By providing the above, the output shaft 21 and the lower case 64 are sealed. This prevents the pressure from escaping.

The fluid inlet 61, when viewed from the rotation axis O of the rotary cylinder member 2, rotates as the rotary cylinder member 2 rotates.
When the pistons 3 and 4 are located at the substantially outer peripheral position of the rotary cylinder member 2, the cylinder parts 22a to 23b are opened to communicate with each other, and when the center line of the rotary cylinder member 2 is at a position of approximately 45 degrees, the cylinder part 22a is formed. To 23b are formed to be closed.

Further, the fluid outlet 62 has a large space 64.
It communicates with the shallow recess 62a formed in the inner wall 64d of b. That is, when the rotary cylinder member 2 rotates as viewed from the rotation axis O of the rotary cylinder member 2, the fluid outlet 62 moves when the pistons 3 and 4 are located at a position where the center line of the rotary cylinder member 2 is approximately 45 degrees. Cylinder parts 22a-23b
Are formed so as to communicate with each other, and the cylinder portions 22a to 23b are formed so as to be closed when the rotary cylinder member 2 is at a substantially outer peripheral position.

The fluid inlet 61 and the fluid outlet 62 are formed so that the flow resistance with respect to the flow of the fluid becomes small and the fluid rotates continuously. For example, a fluid inlet 61 and a fluid outlet 62 are formed at positions facing each other with the rotary cylinder member 2 interposed therebetween so that the fluid can proceed straight as it is without changing its direction in the casing 6. Further, the recess 61 a of the fluid inlet 61 and the recess 62 a of the fluid outlet 62 are formed in a wide range with respect to the rotation direction of the rotary cylinder member 2. For example, the recess 61 a is a cylinder portion (in FIG. 17, the cylinder portion 23 in the state where the pistons 3 and 4 are moved to the outermost side with respect to the rotation direction of the rotary cylinder member 2).
It is formed over the range where the communication hole 61b is formed from the position passing through b). Further, the recess 62a is a cylinder portion in a state where the pistons 3, 4 are moved to the outermost side from the position where the communication hole 62b starts with respect to the rotation direction of the rotary cylinder member 2 (in FIG. 17, the cylinder portion 23
It is formed over the range up to the position immediately before b).
Further, the communication hole 61b of the fluid inlet 61 and the fluid outlet 6
The second communication hole 62b has a passage area sufficiently larger than that of each of the cylinder portions 22a to 23b. In this way, the fluid inlet 61 and the fluid outlet 62 are formed at opposite positions, and the recesses 61a and 62a are formed in a wide range.
Moreover, since the communication holes 61b and 62b are formed to have a large passage area, the flow resistance of the fluid is small.

As shown in FIG. 17, the recess 61a of the fluid inlet 61 and the recess 62a of the fluid outlet 62 form a line passing through the rotation axis O of the rotary cylinder member 2 and the rotation center position X of the piston holding member 5. It is formed so as to be line-symmetrical with respect to each other. The position of the recess 61a on the lower end side in FIG. 17 is formed up to the vicinity of a line passing through the rotation axis O and the rotation center position X,
More specifically, it is located at a position on the fluid inlet side that is approximately half the width of the piston 4 (or 3) from the above line.
Further, the position of the recess 61a on the upper end side in FIG.
1 in the clockwise direction from the line passing between
It is rotated by 35 degrees, and is at a position where it is reduced by approximately half the width of the piston 4 (or 3) in the counterclockwise direction.
Further, since the flow passage cross-sectional areas of the depressions 61a and 62a can be controlled by the value in the depth direction, the fluid resistance is set to be small.

The fluid rotary machine 1 is provided with back pressure relief means. The back pressure relief means is, for example, a piston back-and-forth dynamic back pressure relief means 12 and a cylinder side back pressure relief means 13.
And a piston holding member side back pressure relief means 14.

The piston back-and-forth dynamic back pressure relief means 12 is, for example, a cross groove formed in the center of the bottom surface of the hollow portion 24. The cross groove 12 as the piston back-and-forth dynamic back pressure relief means is formed to be slightly longer than the length of the pistons 3 and 4, and the pistons 3 and 4 are located in the cavity 24 as shown in FIG. Each cylinder part 2 even if
2a-23b can be connected. Therefore, even when an incompressible liquid is used as the fluid, the pistons 3 and 4 are not locked by the hydraulic pressure, and a smooth movement is possible. The cross-sectional area of the cross groove 12 is sufficiently smaller than the cross-sectional area of the pistons 3 and 4, so that the cross section of the cross groove 12 extends from the fluid inlet 61 to the cylinder portions 22a to 23b.
Since the pressure of the fluid that has flowed in acts almost on the pistons 3 and 4, the efficiency of the fluid rotating machine 1 is not deteriorated. However, the cross groove 12 as the piston back-and-forth dynamic back pressure relief means may be omitted, for example, when gas is used as the fluid.

The cylinder-side back pressure releasing means 13 releases the back pressure generated between the rotary cylinder member 2 and the lower case 64 during the operation of the fluid rotating machine 1 to smooth the rotation of the rotary cylinder member 2 and the like. The holes 13 (FIG. 17) that penetrate the four pedestals 25, for example. However, the cylinder-side back pressure relief means is not limited to the hole 13 penetrating the base portion 25, and, for example, as shown in FIGS.
It may be a groove 13 formed on the outer peripheral surface of the rotary cylinder member 2, or, as shown in FIGS. 21 (A) and 21 (B),
The groove 13 formed in the inner wall 64d of the lower case 64 may be used. These three types of cylinder-side back pressure relief means 13 have a structure in which the back pressure is released by making the pressure on both sides of the rotary cylinder member 2 uniform, and it is possible to prevent fluid from leaking out of the casing 6. . When the fluid can be allowed to leak to the outside of the casing 6, the through hole 13 is formed in the lower case 64 as a cylinder side back pressure relief means, as shown in FIGS. 22 (A) and 22 (B), for example. Alternatively, the back pressure may be released to the outside of the casing 6.

Back pressure relief means 14 on the piston holding member side
Is for releasing the back pressure generated between the piston holding member 5 and the upper case 63 during the operation of the fluid rotating machine 1 to smooth the rotation of the piston holding member 5. For example, the piston holding member 5 is penetrated. It is a hole 14 (FIG. 17) to be formed. However,
The piston holding member side back pressure relief means is not limited to the hole 14 penetrating the piston holding member 5, but may be a groove 14 formed on the outer peripheral surface of the piston holding member 5 as shown in FIGS. 20 and 41, for example. Well, or Figure 21 (A)
Further, as shown in FIG. 21B, the groove 14 formed on the inner peripheral surface of the upper case 63 may be used. These three types of back pressure relief means 14 on the piston holding member side have a structure for releasing the back pressure by making the pressures on both sides of the piston holding member 5 uniform, and prevent fluid from leaking to the outside of the casing 6. You can Further, when the fluid can be allowed to leak out of the casing 6, for example, FIG.
As shown in FIG. 2 (B), the through hole 14 may be formed in the upper case 63 as the back pressure relief means on the piston holding member side so that the back pressure is released to the outside of the casing 6.

Further, the fluid rotating machine 1 includes the lubricant circulating mechanism 1
It is equipped with 5. As shown in FIG. 24, for example, the lubricant circulating mechanism 15 communicates with a lubricant tank 16 and a rear surface of the rotary cylinder member 2, and a lubricant inflow passage for guiding the lubricant from the lubricant tank 16 into the casing 6. 17 and the rear surface of the piston holding member 5 are communicated with each other, and the lubricant tank 1
6 is provided with a lubricant outflow passage 18 for guiding the lubricant. A filter (not shown) is provided in the middle of the lubricant inflow passage 17. The lubricant may be any lubricant having lubricity such as lubricating oil, lubricating grease, water, gas and other fluids.

The lubricant inflow passage 17 is connected to the port 19 provided in the upper case 63. This port 19
The lubricant introduced into the upper case 63 from the casing 6
The sliding surface is lubricated through the gaps among the internal members, the cylinder side back pressure relief means 13, the piston holding member side back pressure relief means 14, and the like. Then, it flows out from the port 20 provided in the lower case 64 to the lubricant outflow passage 18, and is circulated to the lubricant tank 16. This lubricant utilizes the pressure difference generated by the rotation of the rotary cylinder member 2 and the piston holding member 5, and the lubricant tank 16 → the lubricant inflow passage 17 →
Inside casing 6-> lubricant outflow passage 18-> lubricant tank 1
Cycle to 6.

Fluid rotating machine 1 configured as described above
Are rotated by the pressure of the fluid. That is, when the fluid is supplied to the fluid inlet 61, the piston holding member 5, the rotary cylinder member 2 and the like make a rotational motion, and the rotational force can be taken out from the output shaft 21.

The operation of the fluid rotating machine 1 shown in FIGS. 16 to 18 will be described with reference to FIGS. 23 (A) to 23 (F).

First, in the state shown in FIG. 23A, the piston 3 that apparently reciprocates inside the cylinder parts 22a and 22b.
Are located in the hollow portion 24 of the rotary cylinder member 2.
In this position, the piston 3 has the cylinder parts 22a, 22
It is engaged with b at the same time. On the other hand, the cylinder portion 23a,
The piston 4 which apparently reciprocates inside 23b is in a state of being advanced (pushed) to the outermost peripheral end of the cylinder portion 23b of the rotary cylinder member 2.

In this state, the cylinder portion 22b faces the recess 61a of the fluid inlet 61, and the cylinder portion 22a faces the recess 62a of the fluid outlet 62.
The cylinder parts 23a and 23b face each other between the recesses 61a and 62a, that is, at positions where the recesses 61a and 62a are not formed.

In this state, when the fluid flows from the fluid inlet 61 into the cylinder portion 22b, the piston 3 is pushed toward the cylinder portion 22a by the pressure of this fluid. Since the rotation center position X1 is deviated from the rotation center position X, the force that the piston 3 advances becomes the force that rotates the piston holding member 5 that holds the piston 3, and the piston holding member 5 moves around the rotation center position X. Rotate.
As a result, the piston 3 rotates about the rotation center position X, so that the rotation cylinder member 2 rotates about the rotation axis O.

The piston 3 discharges the fluid in the cylinder portion 22a from the fluid outlet 62, while the fluid inlet 61 is discharged.
It is pushed forward by the pressure of the fluid that has flowed into the cylinder portion 22b from. On the other hand, as the piston holding member 5 rotates, as shown in FIG. 23 (B), the piston 4 in the cylinder portion 23b is pulled back toward the hollow portion 24. Through the cross groove 12 from the cylinder portion 23b to the other cylinder portions 22a to 22a.
23a, and the rotation of the piston holding member 5 causes the cylinder portion 23b to be recessed 61a in the fluid inlet 61.
Begins to overlap (oppose) with the fluid inlet 6
The fluid starts to flow from 1 to the cylinder portion 23b. That is, the fluid pressure does not hinder the movement of the pistons 3 and 4 (locks the fluid pressure), the pistons 3 and 4 move smoothly, and the piston holding member 5 and the rotary cylinder member 2 rotate smoothly.

Then, the liquid flowing from the fluid inlet 61 into the cylinder portion 22b pushes the piston 3 to continue to rotate the piston holding member 5 and the rotary cylinder member 2. More specifically, the piston 3 has a fluid inlet 6
The fluid pressure from the recess 61a of the No. 1 advances from the position of the rotation axis O of the rotary cylinder member 2 to the outer periphery, and tries to push out the fluid in the cylinder portion 22a on the communication hole 62b side.

Further, when the fluid pressure pushes the piston 3, it becomes a rotational force of the piston holding member 5.

On the other hand, in this state, the piston 4 hardly contributes to the rotation of the rotary cylinder member 2. That is, the piston 4 moves from the fluid inlet 61 to the cylinder portion 2
The fluid flowing into 3b tries to move toward the rotation axis O of the rotary cylinder member 2, but the front and rear of the piston 4 are both connected to the recess 61a, and the pressure is balanced. Rotation is given (FIG. 23 (C)). In this state, the cylinder portion 22b and the cylinder portion 23b overlap the recess 61a of the fluid inlet 61, but the piston holding member 5 and the rotary cylinder member 2 are further rotated, and the state shown in FIG.
When the position is reached, only the cylinder chamber 23b is overlapped with the recess 61a of the fluid inlet 61, and thereafter, the fluid pressure acts on the piston 4.
That is, the fluid pressure pushes the piston 4, the piston 4 pushes the fluid in the cylinder portions 22b and 23a, and the cavity portion 24, the piston 3 is pushed, and the rotational force continues. In other words, the piston receiving the fluid pressure moves from the piston 3 to the piston 4, and the piston holding member 5 and the rotary cylinder member 2 continue to rotate.

On the other hand, in this state, the cylinder chamber 22a is the only cylinder chamber that overlaps the recess 62a of the fluid outlet 62, and the fluid in the cylinder portion 22a is discharged from the fluid outlet 62. When the piston holding member 5 and the rotary cylinder member 2 are further rotated, as shown in FIG.
When the position (E) is reached, the cylinder portion 23a also overlaps the recess 62a of the fluid outlet 62, and the piston 4 receives the fluid pressure from the recess 61a.
The piston holding member 5 is rotated so that the cylinder portion 22a
The fluid inside the cylinder portion 23a and the fluid inside the cylinder portion 23a
The piston holding member 5 and the rotary cylinder member 2 rotate while discharging from 2 (FIG. 23 (F)).

Then, thereafter, the recess 61 of the fluid inlet 61
The positional relationship of the cylinder chamber with respect to a and the recess 62a of the fluid outlet 62 is cylinder portion 22b → cylinder portion 23b →
The piston holding member 5 is changed by sequentially changing from the cylinder portion 22a to the cylinder portion 23a to the cylinder portion 22b, and by alternately changing the piston mainly receiving the fluid pressure from the piston 3 to the piston 4 to the piston 3. And the rotary cylinder member 2 continues to rotate. Therefore, the output shaft 2
The rotational force is continuously output from 1. That is, it functions as a fluid motor.

In this fluid rotary machine 1, the pistons 3 and 4 are moved from the outer side positions of the cylinder parts 22a to 23b to the hollow part 24.
When it is pulled back toward, that is, the cylinder portion 22a-
When the volume in 23b increases, the cylinder portion 22
a to 23b overlap the recess 61a of the fluid inlet 61. Further, when the pistons 3 and 4 are pushed from the hollow portion 24 toward the outer positions of the cylinder parts 22a to 23b, that is, when the volume in the cylinder parts 22a to 23b decreases, the cylinder parts 22a to 23b are filled with fluid. The recess 62a of the outlet 62 overlaps. Therefore, the pistons 3 and 4 move smoothly.
Further, as described above, the fluid inlet 61 and the fluid outlet 6
2 are formed at opposite positions, and the depression 61
Since a and 62a are formed in a wide range and the communication holes 61b and 62b have a large passage area, the flow resistance of the fluid is small. As a result, the fluid pressure is efficiently converted into the rotational force of the rotary cylinder member 2, that is, the output shaft 21, and the fluid rotary machine 1 with high efficiency is obtained.

In this fluid rotating machine 1, the revolving rotary motion of the pistons 3, 4, that is, the rotary motion of the piston holding member 5 about the rotational center position X is performed by the rotary cylinder member 2.
The rotational motion is twice as fast as the angular velocity about the rotation axis O.

Further, the piston 3 is the rotary cylinder member 2
Since the cylinder part 22a, 22b makes one reciprocation and makes one revolution with respect to the support shaft 52 during one revolution of the, the number of revolutions of the piston 3 and the number of revolutions of the rotating cylinder member 2 have a 1: 1 relationship. There is. That is, the ratio of the number of rotations of the rotary cylinder member 2 to the number of rotations of the piston holding member 5 to the number of rotations of the pistons 3 and 4 with respect to the support shafts 52 and 53 is 1: 2: 1.

Further, as described above, since the cross-sectional shapes of the pistons 3 and 4 and the cylinder portions 22a to 23b are the same, when the fluid rotary machine 1 is assembled, the cylinder portions 22a to 23b are fitted. On the other hand, the piston 3,
The upper surface, both side surfaces, and the bottom surface of the piston 4 come into surface contact over the entire length of the pistons 3 and 4, so that the cylinder parts 22a to 23b.
The airtightness and the liquidtightness between the piston and the pistons 3 and 4 are secured.
That is, it is possible to more reliably prevent the fluid from leaking, and it is possible to provide an efficient fluid rotating machine.

Next, an embodiment of a fluid power generator using the fluid rotating machine 1 will be described. In addition, in this embodiment, the fluid rotary machine 1 as a drive source excluding the generator command is used.
1 has basically the same configuration and principle as the configuration described in the embodiment shown in FIGS. 1 to 4, and therefore, the same reference numerals are given and the description thereof is omitted. 25 to 31 show an example of the fluid power generator 70. In this fluid power generator 70, a power generation mechanism is connected to the output side of the fluid rotating machine 1 and these are housed in a casing 6. The power generation mechanism includes a yoke 73 and a magnet 74 that are elements on the rotating side, and a stator core 76, a winding 77, and a holder 78 that are elements on the stationary side.

That is, the rotary cylinder member 2 has a cylindrical portion 7
2 is integrally molded, and the yoke 73 and the magnet 74 are bonded and fixed to the cylindrical portion 72. The rotating cylinder member 2 includes a bearing 7 that receives the thrust direction and the radial direction at the same time.
It is rotatably supported by the lower case 64 via the shaft 5.
On the other hand, the stator core 76 and the winding wire 77 facing the magnet 74 are installed in a holder 78 attached to the lower case 64.

In this embodiment, as shown in FIG. 42, the center position of the salient pole of the stator core 76, the center position of the magnetic pole (N pole or S pole) of the magnet 74, and the cylinder portion 22.
The groove positions of a to 23b are substantially matched. This is to improve maneuverability, and the cylinder portion 22a
When ~ 23b is stopped, maximum torque is generated and it can be easily started. However, as long as there is no problem in use, the above positional relationship is not fixed.

The piston holding member 5 is supported by the upper case 63 via a bearing 79 that simultaneously receives the thrust direction and the radial direction. Upper case 63 is lower case 6
4 are screwed to each other, and an O-ring 80 seals between them. The casing 6,
The pistons 3, 4, the piston holding member 5, the rotary cylinder member 2 and the like are thinned to stabilize the shape and reduce the weight.

When the fluid is supplied to the fluid inlet 61 of the fluid power generator 70, the rotary cylinder member 2 is rotated by the same principle as the operation principle shown in FIG. 23, and the magnet 74 fixed to the rotary cylinder member 2 is rotated by the stator core 76. It rotates with respect to the winding wire 77 wound around. Therefore, an electric current is generated in the winding wire 77 to generate electricity. In this fluid power generator 70,
Since the magnets 74 are arranged around the inner stator core 76 and the winding 77, the power generation efficiency is improved.

The output 62 of the fluid may be used as the inflow port of the fluid, and the inlet 61 of the fluid may be used as the outflow port of the fluid to obtain the reverse rotation output from the output shaft 21.

Further, by making the cross-sectional shapes of the pistons 3 and 4 and the cross-sectional shapes of the cylinder parts 22a to 23b coincide with each other, fluid is prevented from leaking from the periphery of the pistons 3 and 4.

The shapes of the pistons 3 and 4 and the cross-sectional shapes of the cylinder portions 22a to 23b are not limited to those shown in FIG. 19, and, for example, as shown in FIGS. Alternatively, it may have a cross-sectional shape of various irregular shapes such as a smooth U shape, a home base trapezoidal shape, and an inverted triangular shape, and FIG. 37 (A) and FIG.
It may have a square shape as shown in FIG. Further, other shapes may be used.

Further, as shown in FIG. 39, the rotary shaft of the rotary cylinder member 2 may be used as the output shaft 21, and the support shaft 51 on the piston holding member 5 side may be used as the output shaft. That is, the rotation of at least one of the rotary cylinder member 2 and the piston holding member 5 may be output. 38 and 39.
16 shows a cross section at the same position as in FIG. 16, and illustration of the inflow port, outflow port, etc. is omitted.

In the above description, the rolling bearing members 7a and 7b are used to support the rotary cylinder member 2, but the sliding bearing member may be used to support the rotary cylinder member 2. . In addition, the rolling bearing member 8
Although the piston holding member 5 is supported by using a and 8b, the piston holding member 5 may be supported by using a sliding bearing member.

In the above description, the number of cylinder chambers is two (the number of cylinder parts is four) and the number of pistons is two, but the number of cylinders is not limited to this combination. For example, the number of cylinder chambers may be three (the number of cylinder parts is six), and the number of pistons may be three. The operating principle in this case will be briefly described with reference to FIG.

In the example of FIG. 40, six cylinder parts 22a, 22b, 23a, 23b, 28 are provided in the casing 6.
A rotary cylinder member 2 including a and 28b and six fan-shaped base portions 25 is rotatably arranged. That is, in this example, the cylinder parts 22a and 22b and the cavity 24 form the cylinder chamber 22, the cylinder parts 23a and 23b and the cavity 24 form the cylinder chamber 23, and the cylinder parts 28a and 28a.
A cylinder chamber 28 is formed by 28b and the hollow portion 24. Then, at the eccentric position of the rotary cylinder member 2,
A piston holding member 5 is rotatably arranged, and three pistons 3, 4, 9 are rotatably held by the piston holding member 5. As in the case described above, the ratio of rotation between the rotary cylinder member 2 and the piston holding member 5 arranged in the casing 6 of the fluid rotary machine 1 is such that the rotation number of the piston holding member 5 is two. Cylinder member 2
Is 1, the number of reciprocations of the pistons 3, 4, 9 in the cylinder chambers 22, 23, 28 is 1, and the number of revolutions of the piston with respect to a support shaft (not shown) is also 1.

Also in this example, as in the case of FIG. 23, when the pistons 3, 4, 9 rotate clockwise in the drawing due to the rotation of the piston holding member 5, the rotary cylinder member 2 also moves in the same direction in accordance with this operation. It is designed to rotate. As a result, the piston 3 reciprocates visually while traversing the cavity 24, the piston 4 in the cylinder chamber 23, and the piston 9 in the cylinder chamber 28.

The longitudinal dimension of each piston 3, 4, 9 is such that it can engage with both the inner walls of the cylinder chambers on both sides of the cavity 24 when traversing the cavity 24. There is. Therefore, the pistons 3, 4, 9 simultaneously contact the cylinder chambers on both sides when traversing the cavity 24. Of course, each piston 3, 4, 9 is designed so as not to collide with the other pistons 3, 4, 9 when traversing the cavity 24. As a result, in the example of FIG. 40, the pistons 3, 4, 9 rotate while being constantly guided by one of the cylinder chambers, and as a result, the pistons 3, 4, 9 move in the respective cylinder chambers 2.
2, 23, 28 are surely put in and out, and a motor operation for rotating an output shaft (not shown) by the pressure of the fluid is performed. When the working fluid is an incompressible fluid, although not shown, six shallow grooves extending radially may be formed in the cavity 24 where the cylinder chambers 22, 23 and 28 intersect. That is, as the piston back-and-forth dynamic back pressure relief means, a groove having a shape that radiates in six isotropic directions (not shown) may be provided in the cavity portion 24.

The fluid rotary machine 1 of the type having the three cylinder chambers 22, 23, 28 and the three pistons 3, 4, 9 as shown in FIG. 40 has little torque fluctuation.

Next, FIGS. 43 to 47 show an embodiment in which the rotary cylinder device of the present invention is configured as a rotary compressor for compressing a fluid by inputting a rotational force. The fluid to be pumped in this embodiment is not limited to a liquid such as oil or water, but may be a gas such as air or gas. In addition, the same reference numerals are attached to the components having basically the same configurations and principles as the configurations described in the embodiments shown in FIGS. 1 to 4 and 16 to 18, and the description thereof will be omitted.

The pistons 3 and 4 of this embodiment are made of, for example, sintered metal (sintered body of powder of metal or the like). Therefore, the pistons 3 and 4 become porous,
It can be impregnated with lubricating oil in advance, which is advantageous for lubricating the sliding surface. However, it goes without saying that the pistons 3 and 4 may be formed using a material other than sintered metal.

In this embodiment, the rotation of the support shaft 21 as an input shaft is transmitted to the rotary cylinder member 2 via the Kelet plate 221. More specifically, the piston holding member 5 is provided in each base portion 25 of the rotary cylinder member 2.
44 and FIG. 4 are opposite to the surface opposite to FIG.
5, a large diameter hole 25a opening to the lower side surface is formed. Then, in each of the large diameter holes 25a, the two large diameter holes 25a that are linearly arranged are inserted with the Kerley shaft 30 that is erected and fixed to the Keret plate 221. With respect to the Kelet shaft 30, the large diameter hole 25a is provided in the cylinder portion 22.
a, 22b, 23a, 23b are formed slightly longer in the axial direction, and even if the rotation centers of the rotating cylinder member 2 and the Keray plate 221 are deviated, the rotation of the Keray plate 221 is rotated while absorbing the deviation. It can be satisfactorily transmitted to the cylinder member 2. A clearance is provided between the kelet plate 221 and the rotary cylinder member 2 to allow tilt adjustment of the kelet plate 221 as described later.

The input shaft 21 is inserted and fixed to the rotation axis of the Kelet plate 221 by press fitting. The center of the input shaft 21 is rotatably supported by the sliding bearing member 7. Further, the tip of the input shaft 21 projects to the outside of the casing 6.

The rotary cylinder member 2 includes the bearing plate 3
It is rotatably supported by 2. The bearing plate 32 is a member for flatly rotatably receiving the rotary cylinder member 2, and has two projections 32a and 32b formed on its receiving surface, as shown in FIG. Each protrusion 32
The parts a and 32b are partially cut to facilitate the circulation of the lubricating oil. Further, the cut portion of each of the protrusions 32 a and 32 b is 90
The rotation cylinder members 2 are arranged so as to be offset from each other to prevent the rotation cylinder member 2 from being tilted. In this way, the rotary cylinder member 2 can be flatly received near its outer periphery,
The rotating state of the rotating cylinder member 2 becomes stable,
It becomes difficult to tilt, the compression performance can be secured, and the reliability can be improved. The bearing plate 32 is formed with a hole 32c for circulating lubricating oil, which will be described later.

The inclination of the bearing plate 32 depends on the adjustment screw 3
It is adjustable by 3. The adjusting screw 33 is composed of, for example, three push screws 33a and three pull screws 33b, and these are arranged alternately in the circumferential direction. The push screw 33a causes the bearing plate 32 to partially approach the rotating cylinder member 2, and the pull screw 33b causes the bearing plate 32 to partially move away from the rotating cylinder member 2. Therefore, the push screw 33a and the pull screw 3
The inclination of the bearing plate 32 can be adjusted by changing the screwing amount of 3b. For this reason, the component accuracy in the thrust direction can be reduced. An O-ring 43 is provided between each adjusting screw 33 and the lower case 64 and the bearing plate 32.
Is sealed by. Further, a hole 32c for circulating the lubricating oil is formed.

The piston holding member 5 is the Keret plate 2
It is rotatably supported by a bearing plate 134 similar to the bearing plate 32 supporting 21. As with the bearing plate 32, the bearing plate 134 also has two protrusions 134a and 134b,
The piston holding member 5 is adapted to receive a flat surface in the thrust direction. In this way, the piston holding member 5 can be flatly received in the vicinity of its outer circumference, so that the rotation state of the piston holding member 5 becomes stable, tilting becomes difficult, compression performance can be secured, and reliability is improved. be able to. In addition, the hole 13 for circulating the lubricating oil
4c is formed. And this bearing plate 1
The inclination of 34 can be adjusted by an adjusting screw 33 including, for example, three push screws 33a and three pull screws 33b. Therefore, the accuracy of parts in the thrust direction can be reduced. Each adjusting screw 33 and upper case 6
3, the bearing plate 33 and the bearing plate 33 are sealed by an O-ring 42.

The rotary cylinder member 2 is supported by the peripheral wall 64d of the lower case 64 and the piston holding member 5 is supported by the peripheral wall 63d of the upper case 63 in the radial direction.

Support shaft internal passages 52a and 53a are formed in the support shafts 52 and 53 so as to penetrate the support shafts 52 and 53 in the axial and radial directions. A part of the lubricating oil, which will be described later, is part of the support shaft passage 5
It flows through 2a and 53a and lubricates the sliding surface between the pistons 3 and 4 and the piston holding member 5 and the sliding surface between the support shafts 52 and 53 and the pistons 3 and 4.

The support shaft inner passages 52a and 53a may be omitted depending on the degree of lubrication.

The upper case 63 and the lower case 64 are fixed by screws 45. An O-ring 35 seals between the upper case 63 and the lower case 64.

The bottom portion of the lower case 64 is provided with an insertion hole 64e for allowing the input shaft 21 to pass therethrough. Also,
The cap 36 is fixed to the bottom of the lower case 64 by screws 37. Between the lower case 64 and the cap,
It is sealed by an O-ring 38. Further, the seals inside the input shaft 21 and the compressor are sealed by a two-stage stacked mechanical seal 99.

The recess 61a of the suction port 61 which is the fluid inlet
The pistons 3, 4 as the rotary cylinder member 2 rotates.
Is formed so as to start from a position slightly inside the position where the piston has moved to the outermost circumference and reach a position where the pistons 3 and 4 have moved to the vicinity of the hollow portion 24. Further, the recess 62a of the discharge port 62, which is the outlet of the fluid, is slightly provided at a position slightly before the position where the pistons 3 and 4 move to the outermost circumference as the rotary cylinder member 2 rotates. As described above, the recess 62a is larger than the recess 61a in the rotary cylinder member 2
Is formed in an extremely narrow range with respect to the rotation direction of the.
Therefore, the cylinder parts 22a, 22b, 23a, 2
These cylinder parts 22a, 22b, 23a, 23b do not face the recess 62a until the pressure in 3b is sufficiently increased, and the fluid in the cylinder parts 22a, 22b, 23a, 23b compressed by the pistons 3, 4 Can be discharged at once from the discharge port 62 while maintaining a high pressure.

The pistons 3 and 4 are located at the outermost position (see FIG.
9 of the cylinder portion 23b), the cylinder portion 2
The pressure in 2a, 22b, 23a and 23b is the highest. On the other hand, the suction port 61 has a low pressure. Therefore, the cylinder parts 22a, 22 at the outermost peripheral positions of the pistons 3, 4 are
Although fluid leakage from b, 23a, and 23b to the suction port 61 is considered, in this rotary compressor 1, the partition between the outermost peripheral positions of the pistons 3 and 4 and the recess 61a of the suction port 61 (see FIG. 49). A) is sufficiently widened to prevent fluid leakage. Further, the discharge port 62 has a substantially equal pressure as compared with the cylinder parts 22a, 22b, 23a, 23b at the outermost peripheral positions of the pistons 3, 4, but when the rotary cylinder member 2 rotates from the outermost peripheral positions of the pistons 3, 4. Since the volumes of the cylinder parts 22a, 22b, 23a, 23b increase and the pressure decreases, the partition part (part B in FIG. 49) between the outermost peripheral position and the recess 62a of the discharge port 62 is sufficiently widened to allow fluid leakage. Is preventing.

The discharge port 62 has, for example, a ball 39.
A check valve 39 including a and a spring 39b is provided to prevent the reverse flow of fluid. The check valve 39 is arranged at a position close to the recess 62a, and reduces the volume of the check valve 39 on the upstream side to increase the compression ratio.

This rotary compressor 1 also has a back pressure relief means. In this embodiment, the back pressure relief means includes, for example, a cylinder side back pressure relief means 13 and a piston holding member side back pressure relief means 14.

The cylinder-side back pressure relief means 13 is provided with the rotary cylinder member 2 and the lower case 64 while the rotary compressor 1 is in operation.
This is for releasing the back pressure generated during the rotation of the rotary cylinder member 2 and smoothing the rotation of the rotary cylinder member 2 and the like, and is, for example, the hole 13 penetrating the four pedestals 25 and communicating with the large diameter hole 25a. However,
The cylinder-side back pressure relief means is not limited to the hole 13 penetrating the base portion 25, but may be a groove 13 formed on the outer peripheral surface of the rotary cylinder member 2 as shown in FIGS. 50 and 51, or As shown in FIGS. 55 and 56,
The groove 13 formed in the peripheral wall 64d of the lower case 64 may be used.

Back pressure relief means 14 on the piston holding member side
Is for releasing the back pressure generated between the piston holding member 5 and the upper case 63 during the operation of the rotary compressor 1 to smooth the rotation of the piston holding member 5. It is a hole 14 penetrating therethrough. However, as the back pressure relief means on the piston holding member side, the piston holding member 5 is used.
It is not limited to the hole 14 penetrating through, but may be a groove 14 formed on the outer peripheral surface of the piston holding member 5 as shown in FIGS. 50 and 51, or as shown in FIGS. Groove 1 formed on the peripheral wall 63d of the case 63
4 is also acceptable.

The rotary compressor 1 includes the lubricating oil circulation mechanism 1
It is equipped with 5. The lubricating oil circulation mechanism 15 includes, for example, as shown in FIG. 46, an oil tank 16, an oil inflow passage 17 for guiding oil from the oil tank 16 into the casing 6, and an oil tank 16 from the inside of the casing 6.
It has an oil outflow passage 18 for guiding oil to. A filter (not shown) is provided in the middle of the oil inflow passage 17.

The oil inflow passage 17 is connected to the joint 19 attached to the port 63a of the upper case 63. The oil introduced from the joint 19 into the upper case 63 through the port 63a is provided in the gaps between the members in the casing 6, the cylinder side back pressure relief means 13, the piston holding member side back pressure relief means 14, the support shaft inner passage 52.
a, 53a, holes 32c of the bearing plates 32, 134,
The sliding surface is lubricated through 134c and the like. Then, the joint 2 attached to the port 64a of the lower case 64
0 to the oil outflow passage 18, and the oil tank 1
It is cycled to 6. This oil is used in the rotating cylinder member 2
And the pressure difference generated by the rotation of the piston holding member 5, the oil tank 16 → the oil inflow passage 17 → the joint 19 → the port 63a → the inside of the casing 6 → the port 6
4a → joint 20 → oil outflow passage 18 → oil tank 16 circulates.

In this embodiment, since the pistons 3 and 4 are made of sintered metal, the lubricating oil impregnated in the pistons 3 and 4 by the back pressure generated by the rotation of the piston holding member 5 and the like. Leaks out of the pistons 3, 4 and slides between the pistons 3, 4 and the piston holding member 5, and the pistons 3, 4 and the cylinder parts 22a, 22b, 2
The lubricating oil lubricates the sliding surface between 3a and 23b.

[0165] The rotary compressor 1 configured as described above.
Then, when the input shaft 21 is driven by a motor or the like (not shown), this rotational force is applied to the input shaft 21 → the Keret plate 22.
1 → Keray shaft 30 → rotating cylinder member 2 → piston 3,
4 → Transmitted to piston holding member 5. This allows
The rotary cylinder member 2 and the piston holding member 5 rotate relative to each other to move the pistons 3 and 4 with respect to the cylinder chambers 22 and 23 to discharge the fluid sucked from the suction port 61 from the discharge port 62. That is, when the input shaft 21 is rotated,
The piston holding member 5, the rotary cylinder member 2 and the like perform a rotational motion with an equal angular velocity ratio, and move the pistons 3 and 4 to increase or decrease the volume in the cylinder parts 22a, 22b, 23a and 23b, and to pump the fluid. .

FIG. 52 shows the operation of the rotary compressor 1.
It demonstrates using (A) -FIG.52 (F). Note that FIG.
52A to 52F show the rotation angle of the rotary cylinder member 2 at intervals of 15 degrees.

This rotary compressor 1 includes the cylinder parts 2
2a, 22b, 23a, and 23b alternately repeat the intake stroke and the compression stroke to compress the fluid. First, the intake stroke will be described focusing on the cylinder portion 23b. When the rotary cylinder member 2 and the piston holding member 5 rotate relative to each other, the piston 4 moves from the outermost peripheral position of the cylinder portion 23b shown in FIG. 52 (A) toward the cavity 24 (FIG. 52 (B)). Then, when the piston holding member 5 and the rotary cylinder member 2 rotate to the position shown in FIG. 52 (C), the cylinder portion 23b opposes (overlaps) the recess 61a of the suction port 61, so that the negative force accompanying the movement of the piston 4 The fluid moves from the suction port 61 to the cylinder portion 23
It is sucked into b (FIGS. 52D to 52F). Then, when the piston holding member 5 and the rotary cylinder member 2 are further rotated, the cylinder portion 23b is recessed in the suction port 61.
1a, the intake stroke ends, and the cylinder portion 23b is changed to the cylinder portion 22a in FIG. 52 (A).
When it is rotated to the position, the compression stroke is started.

This compression stroke will be described focusing on the cylinder portion 22a. When the piston holding member 5 rotates due to the rotation of the rotary cylinder member 2, the piston 3 moves into the hollow portion 24.
The cylinder portion 22a enters from the position (see FIG. 52).
(A), FIG. 52 (B)). And the rotary cylinder member 2
By further rotation of the piston holding member 5 and the piston 3,
Moves toward the outer position in the cylinder part 22a (FIGS. 52 (C) and 52 (D)).
The fluid in 2a is compressed. When the fluid is sufficiently compressed (FIG. 52 (E)), the cylinder portion 22a overlaps with the recess 62a of the discharge port 62 (FIG. 52).
(F)), The fluid in the cylinder part 22a is pressure-fed by opening the check valve 39.

Then, the above operation is performed for each cylinder portion 22.
Since a, 22b, 23a, and 23b are sequentially repeated, the pistons 3 and 4 compress and deliver the fluid one after another.

The rotary compressor 1 can be used as a compressor of a cooling circuit composed of, for example, an evaporator, a condenser, a capillary tube, a heat radiation pipe and the like. That is,
It can be used to compress and circulate the heat-exchanged refrigerant. In addition, the motor that rotates the input shaft 21
It may be housed in the casing 6.

In the embodiment of FIG. 44, of the rotary cylinder member 2 and the piston holding member 5, the input shaft 21 is arranged on the rotary cylinder member 2 side to transmit the rotation, but on the piston holding member 5 side. Alternatively, the rotation of the input shaft 21 may be transmitted.

Further, in the embodiment of FIG. 43, the rotary cylinder member 2 and the piston holding member 5 are supported by the bearing plates 32 and 134 which are sliding bearings, but a rotary cylinder such as a ball bearing is used. The member 2 and the piston holding member 5 may be supported.

The bearing plates 32 and 134 shown in FIG. 53 may be used.

In the embodiment of FIG. 43, the support shafts 52 and 53 are directly inserted into the holes 3a and 4a of the pistons 3 and 4, but the guide piece 44 may be interposed between them. good. The guide piece 44 is shown in FIG. Between the guide piece 44 and the holes 3a, 4a of the pistons 3, 4, there is a slight rattling in the piston width direction. Therefore, even if the shaft centers of the support shafts 52, 53 and the pistons 3,
Even if the rotation center positions X1 and X2 of the piston 4 are deviated, the pistons 3 and 4 can be rotated around the rotation center position X while absorbing the deviation. Therefore, it is possible to reduce the processing accuracy of the required parts, facilitate the processing, and reduce the manufacturing cost.

Further, in the embodiment of FIG. 43, the inclination of the bearing plates 32 and 134 is adjusted by the adjusting screw 33, but the adjusting screw 33 may be omitted when the accuracy of parts can be secured. .

In the embodiment of FIG. 43, the input shaft 21
The Kerley plate 221 and the Kerley shaft 30 are interposed between the rotation cylinder member 2 and the rotation cylinder member 2, but when the component accuracy can be ensured, the Kerley plate 221 and the Kerley shaft 30 are omitted and input to the rotation cylinder member 2. The shaft 21 may be attached.

Although the O-ring is used as the seal structure in the embodiment of FIG. 43, a mechanical seal or the like may be used. Further, if the drive motor and the input shaft are directly connected and put in a pressure vessel (not shown), an O-ring may be omitted.

Further, the number of cylinder parts may be six and the number of pistons may be three. That is, as shown in FIG.
Six cylinder parts 22a, 22b, 23a, 23b,
28a, 28b and three pistons 3, 4, 9 may be provided. The relationship between the movements of the pistons 3, 4, 9 and the cylinder chambers 22, 23, 28 in this case is the same as in the example of FIG. 40, and the description thereof is omitted.

Also, a plurality of rotary compressors 1 may be combined to form a multi-stage type. By flowing the compressed fluid into the next-stage compressor 1, it is possible to obtain a higher-pressure fluid.

The above-mentioned embodiment is an example of the preferred embodiment of the present invention, but the present invention is not limited to this, and various modifications can be made without departing from the gist of the present invention.
For example, it is not necessary to equally distribute the cylinder parts to the rotary cylinder member 2 in the circumferential direction, and for example, as shown in FIG. 57, the cylinder parts 22a, 22b, 23a, 23 are arranged.
b does not have to be equally distributed in the circumferential direction with respect to the rotary cylinder member 2.

Further, as shown in FIG. 58, the cylinder parts 22a, 22b, 23a and 23b are connected to the rotary cylinder member 2.
It may be formed by being offset with respect to the rotation axis O. Although not shown, the width of the piston may be different.

Further, a magnet may be arranged on the base of the piston or the rotary cylinder member to prevent the fluid from leaking from the gap between them due to the magnetic fluid.
The concept of such a configuration is shown in FIG. 59, for example. A magnet 590 is arranged in the piston 3, and the magnet 59
The magnetic fluid 591 is attached to 0. Magnet 59
0 is installed in the vicinity of the contact portion of the piston 3 with the cylinder chamber, in the center of the piston 3 in this embodiment.
With such a configuration, each magnet 590 attracts the magnetic fluid 591 to the piston 3 and holds the magnetic fluid 591 on the outer periphery thereof, thereby filling the magnetic fluid 591 with the gap between the rotary cylinder member 2 and preventing the fluid from leaking from the gap. can do. In the figure, reference characters N and S denote magnets 590.
The magnetic poles of

The magnet 5 placed on the piston 3
The shape of 90 may be as shown in FIG. Further, instead of disposing the magnet 590 on the piston 3, the magnet 590 may be arranged on the base portion 25 of the rotary cylinder member 2 as shown in FIGS. 61 and 62, for example.

Further, for example, as shown in FIG. 63, the corner 24a of the hollow portion 24 of the rotary cylinder member 2 may be chamfered. By chamfering in this way, when the pistons 3 and 4 pass through the hollow portion 24 of the rotary cylinder member 2, even if the directions of the pistons 3 and 4 with respect to the traveling direction are inclined, they move smoothly to the next cylinder chamber. can do. In this case, the corners of the pistons 3 and 4 may be chamfered,
It is more desirable to chamfer the rotary cylinder member 2 side as shown in FIG. 63 than to chamfer the pistons 3 and 4 side. When chamfering is applied to the piston side, even if the piston rotates to the outermost peripheral side of the rotary cylinder member, the chamfered portion will leave a gap and compressed fluid will remain. Because it will be carried over to the process of, and efficiency will deteriorate. In particular, when the rotary cylinder device of the present invention is applied to a compressor, not only the remaining fluid lowers the efficiency of the compressor, but also the residual fluid in a compressed state is communicated with the intake port to rapidly increase the efficiency. It expands and causes noise and vibration. On the other hand, by chamfering the rotary cylinder member side and making the corners of the piston corners, the residual volume of the highest pressure fluid at the cylinder outermost position can be reduced, and the efficiency of the compressor is reduced. Without
The piston can move smoothly.

The back pressure relief means may be the passages 580 and 581 shown in FIGS. 64 to 66, for example. That is, for example, as shown in FIGS. 64 to 66, a passage 580 that communicates both front and back surfaces of the rotary cylinder member 2 and a passage 581 that communicates both front and rear surfaces of the piston holding member 5 may be formed. In this case, it goes without saying that the shapes and sizes of the passages 580 and 581 are not particularly limited. Further, the depression 582 may be formed on the upper surface of the base portion 25 of the rotary cylinder member 2, or the depression 583 may be formed around the opening of the passage 581 of the piston holding member 5. In this case, each recess 582,
Of course, the shape and size of 583 are not particularly limited.

Further, a rotational speed detecting means for detecting the rotational speeds of the rotary cylinder member 2 and the piston holding member 5 may be provided. For example, FIG. 67 shows an example of a case where a fluid power generator as a rotary cylinder device is provided with a rotation speed detecting means.
In this fluid power generator, for example, the piston support shafts 52, 53
Is made of metal, the piston holding member 5 is a separate member, and the piston support shaft 5 of the piston holding member 5 is
The metal sensor 571 is attached at a position facing the Nos.
The number of rotations of the fluid power generator is detected by counting the detection output of (1) with a counter. However, the method is not limited to this. For example, M that detects the rotation of the magnet 572 is used.
An R element, a Hall element 573, or the like may be provided, and the number of detection outputs thereof may be counted by a counter to detect the rotation speed of the fluid power generator. Further, a voltage limiter (not shown) may be provided to detect the rotation speed of the fluid generator based on the sine waveform of the power generation output. Furthermore, a slit plate (not shown) is provided on the outer ring of the magnet 572, and a photo interrupter (not shown) is provided on the case side. The light passing through the slit plate is detected by the photo interrupter, and the detected value is counted by the counter. Alternatively, the rotation speed of the fluid power generator may be detected.

Further, as shown in FIG. 68, for example, a rotary type cylinder device may be provided with a rotation speed detecting means to form a flow meter, for example. Similar to the example of FIG. 67, in this example, the piston support shafts 52 and 53 are made of metal, and the piston holding member 5 is a separate member, and faces the piston support shafts 52 and 53 of the piston holding member 5. A metal sensor 571 may be attached to the position, and the detection output of the piston support shafts 52, 53 by the metal sensor may be counted by a counter. Further, the magnet 572 is attached to the rotary cylinder member 2, and an MR element, a hall element 573, etc. for detecting the rotation of the magnet 572 are provided, and the output of these elements is counted by a counter so that the rotational speed of the flowmeter can be detected. You can Furthermore, a slit plate (not shown) is provided on the outer ring of the magnet 572, and a photo interrupter (not shown) is provided on the case side. The light passing through the slit plate is detected by the photo interrupter, and the detected value is counted by the counter. Alternatively, the rotation speed of the flow meter may be detected. Since the flow rate when the rotary cylinder member makes one rotation is known in the positive displacement type flow meter, the total flow rate can be measured by counting the number of rotations with the counter.

That is, when the rotary cylinder device of the present invention is applied to a flow meter, the flow rate of the fluid can be electrically detected by providing the rotation speed detection means. The electromagnetic on-off valve provided in the passage can be on / off controlled, and an alarm can be sounded when the flow rate reaches a predetermined value.

Further, as shown in FIG. 69, for example, when the rotary type cylinder device of the present invention is used as a fluid pump, rotation speed detecting means may be provided to feedback control the operation of the fluid pump. . That is, the rotation speed may be detected by the same method as that of the flow meter of FIG. 68, and the drive motor 563 may be controlled based on the count value of the counter.

[0190]

As described above, in the rotary cylinder device according to the first aspect of the present invention, the cylinder chamber is formed so as to pass through the rotation axis, and the rotation cylinder member that rotates about the rotation axis and the cylinder chamber are provided. A piston that reciprocates linearly in surface contact, a piston holding member that holds the piston and rotates about a rotation center that is eccentric from the rotation axis of the rotation cylinder member, and rotatably supports the rotation cylinder member and the piston holding member. And a casing having at least one fluid inlet and at least one fluid outlet, and the piston is rotatably held at a position distant from the center of rotation of the piston holding member by a certain distance. When the piston reciprocates in the cylinder chamber, the rotating cylinder member and the piston holding member Each of them can rotate while being supported by the casing, and the piston can also rotate by itself, and it becomes possible for the piston to rotate around the center of rotation and move linearly in the cylinder chamber while changing its position. . As a result, even when the piston is configured to be in surface contact with the cylinder chamber, each member can smoothly rotate. For example, even if the piston has a block shape, each member can smoothly rotate. Therefore, the piston can be easily manufactured, and the accuracy of the piston can be easily obtained.

Further, the contact area between the piston and the cylinder chamber can be made large, and the fluid resistance at the contact surface is large as compared with the conventional one in which the contact surface is formed by so-called line contact, and the airtightness and liquid The tightness is enhanced, and the fluid can be prevented from leaking from the contact surface portion. Therefore, it becomes possible to convert fluid energy into rotational movement or rotational movement into fluid energy with low loss.

Moreover, since the piston reciprocates linearly in the cylinder chamber, the piston operation is smooth and stable, and vibration and noise during rotation are reduced.
In addition, since it is possible to widen the allowable range of component accuracy, it becomes easier to process parts, and conversely, if the level of component accuracy is the same as the conventional level, airtightness and reliability will be improved. Alternatively, when a fluid motor is used, it is easy to improve the performance.

Further, in the rotary cylinder device according to the second aspect of the present invention, a guide portion for guiding the piston in the sliding direction is formed in the cylinder chamber, and a guide engaging portion for engaging the guide portion is formed in the piston. Therefore, the reciprocating linear movement of the piston can be made smooth.

Further, in the rotary type cylinder device according to a third aspect of the invention, the fluid inlet has a casing in one of the regions divided by a line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. Is provided so as to communicate with the cylinder chamber, and the outlet is communicated with the cylinder chamber in the casing in either one of the regions divided by the line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. Since it is provided, it is possible to arrange the inlet and the outlet far enough apart, and even if the pressure difference between the fluid on the inlet side and the fluid on the outlet side is large, this fluid does not pass through the cylinder chamber. Direct flow from the inlet to the outlet or from the outlet to the inlet can be prevented. In particular, by providing an inlet and an outlet for this fluid at positions facing the outer peripheral surface side of the rotating cylinder member of the casing, the respective cylinder chambers and inlet and outlet are connected so that each cylinder chamber communicates with the outer peripheral surface of the rotating cylinder member. It can be configured and the product is better organized.

Further, in the rotary cylinder device according to the fourth aspect, since the surface of the piston facing the piston holding member is a flat surface, the piston moves smoothly with respect to the piston holding member. Further, it is possible to prevent a gap from being generated between the piston and the piston holding member, and prevent fluid leakage.

Further, in the rotary type cylinder device according to the fifth aspect, since the cross-sectional shape of the piston and the cross-sectional shape of the cylinder chamber are similar shapes that form a slight slidable gap, the rotary cylinder member is It is possible to prevent a gap from being generated between the pistons and prevent fluid leakage.

Further, in the rotary type cylinder device according to the sixth aspect, the magnetic fluid is arranged in a gap formed between the piston and the cylinder chamber, and a magnet for holding the magnetic fluid in the gap is provided in the piston and the cylinder chamber. Since it is provided in the vicinity of the contact area with the magnetic fluid, the magnetic fluid held by the magnet is filled in the gap between the piston and the rotating cylinder member, and the slight gap at the portion where the piston and the cylinder member face each other is more reliable. The fluid leakage from the contact portion can be prevented more reliably.

Further, in the rotary type cylinder device according to the seventh aspect, a plurality of pistons and cylinder chambers are formed, and the plurality of cylinder chambers are formed so as to pass through and cross the rotation axis of the rotary cylinder member. Therefore, it is possible to provide a rotary cylinder device that is rotated by a plurality of pistons.

Further, in the rotary type cylinder device according to the eighth aspect, since the cylinder chambers are arranged at positions equidistantly distributed in the circumferential direction of the rotary cylinder member, the rotational balance of the rotary cylinder member is improved, and vibration is improved. It is possible to prevent the occurrence of noise and noise and to provide a rotary cylinder device suitable for high-speed rotation.

Further, in the rotary type cylinder device according to the ninth aspect, the length in the moving direction of the piston at the portion where the plurality of cylinder chambers intersect is shorter than the length of the piston, so that the piston performing the reciprocating linear motion is a cylinder. As the chambers pass through the intersecting portion, they are guided by the wall surface of the moving cylinder chamber to cross another intersecting cylinder chamber, and can smoothly pass without colliding with the other cylinder chambers.

Further, in the rotary type cylinder device according to the tenth aspect, since the chamfered portion is formed at the portion where the plurality of cylinder chambers intersect, passage of the piston at the portion where the cylinder chambers intersect becomes smoother. be able to.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a first embodiment of a rotary cylinder device of the present invention.

FIG. 2 is a plan view of the rotary cylinder device of FIG. 1 with an upper case and a piston holding member removed.

3 is an exploded perspective view showing a rotary cylinder member, a piston holding member, and a piston of the rotary cylinder device of FIG.

FIG. 4 is a view for explaining the operation of the rotary cylinder device of FIG. 1, showing a state in which one piston traverses a cavity and the other piston enters the innermost part of the cylinder chamber.

5 is a view for explaining the operation of the rotary cylinder device of FIG. 1, showing a state in which the rotary cylinder member is rotated 30 degrees clockwise from the state of FIG.

6 is a view for explaining the operation of the rotary cylinder device of FIG. 1, showing a state in which the rotary cylinder member has been rotated clockwise by 30 degrees from the state of FIG.

7 is a diagram for explaining the operation of the rotary cylinder device of FIG. 1, showing a state in which the rotary cylinder member has been rotated clockwise by 30 degrees from the state of FIG.

FIG. 8 is a plan view showing a second embodiment of the rotary cylinder device of the present invention and showing the relationship between the rotary cylinder member and the piston.

FIG. 9 is a plan view showing the third embodiment of the rotary cylinder device of the present invention and showing the relationship between the rotary cylinder member and the piston.

FIG. 10 is a vertical cross-sectional view showing a modified example of the rotary cylinder device according to the first embodiment of the present invention.

FIG. 11 is a side view showing a fourth embodiment of the rotary cylinder device of the present invention, in which a part is cut away.

12 is a plan view of the rotary cylinder device of FIG. 11 with a casing lid removed.

13 is a vertical cross-sectional view of the rotary cylinder device of FIG.

FIG. 14 is an enlarged view showing a part of the bearing.

FIG. 15 is a conceptual diagram showing a relationship between a piston holding member and a locus during rotation of the piston.

FIG. 16 is a vertical sectional view showing an embodiment in which the rotary cylinder device of the present invention is configured as a fluid rotating machine.

FIG. 17 is a plan view showing the fluid rotary machine of FIG. 16 with an upper case and a piston holding member removed.

18 is an exploded perspective view showing a rotary cylinder member, a piston holding member and a piston of the fluid rotary machine of FIG.

FIG. 19 shows a first example of a piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 20 is a view showing a second example of the back pressure relief means, and is a plan view showing the fluid rotary machine with the upper case and the piston holding member removed.

FIG. 21 is a view showing a third example of back pressure relief means,
(A) is a plan view showing the fluid rotating machine with an upper case and a piston holding member removed, and (B) is a BB line of (A).
It is sectional drawing which follows the line.

22A and 22B are views showing a fluid rotating machine to which a fourth example of back pressure relief means is applied, FIG. 22A is a plan view showing a state in which an upper case and a piston holding member are removed, and FIG. B
It is sectional drawing which follows the -B line.

23 is a view for explaining the operation of the fluid rotating machine of FIG.
(A) is a diagram showing a state in which one piston crosses the cavity and the other piston reaches the innermost part of the cylinder chamber, and (B) shows a state in which the rotary cylinder member
The state where the rotary cylinder member is rotated 15 degrees from the state of (B),
(D) is a diagram showing a state where the rotary cylinder member is rotated 15 degrees from the state of (C), (E) is a diagram showing a state where the rotary cylinder member is rotated 15 degrees from the state of (D), (F) )
FIG. 11 is a diagram showing a state in which the rotary cylinder member is rotated 15 degrees from the state of (E).

FIG. 24 is a schematic configuration diagram of a lubricant circulation mechanism.

FIG. 25 is an exploded perspective view of a fluid power generator in which the rotary cylinder device of the present invention is incorporated in a drive source.

FIG. 26 is a plan view of the fluid generator with the upper case and the piston holding member removed.

27 is a cross-sectional view taken along the line AA of FIG.

28 is a bottom view of the fluid power generator of FIG. 25. FIG.

29 is a plan view showing an upper case of the fluid generator shown in FIG. 25. FIG.

30 is a plan view showing a rotary cylinder member of the fluid power generator of FIG. 25. FIG.

FIG. 31 is a plan view showing a yoke and windings of the fluid power generator shown in FIG. 25.

FIG. 32 shows a second example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 33 shows a third example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 34 shows a fourth example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 35 shows a fifth example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 36 shows a sixth example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 37 shows a seventh example of the piston, (A) is a perspective view of the piston, and (B) is a longitudinal sectional view of the piston.

FIG. 38 is a vertical sectional view showing a second embodiment in which the rotary cylinder device of the present invention is configured as a fluid rotating machine.

FIG. 39 is a vertical sectional view showing a third embodiment in which the rotary cylinder device of the present invention is configured as a fluid rotating machine.

FIG. 40 is a diagram for explaining the operation of the fluid rotating machine of the fourth embodiment of the rotary cylinder device of the present invention, in which (A) shows 3
The figure which shows the state which one of two pistons has penetrated to the innermost part of the cylinder chamber, (B) the figure which shows the state which rotated the rotary cylinder member 10 degrees from the state of (A),
(C) is a diagram showing a state where the rotary cylinder member is rotated 10 degrees from the state of (B), (D) is a diagram showing a state where the rotary cylinder member is rotated 10 degrees from the state of (C), (E) )
FIG. 6A is a diagram showing a state where the rotary cylinder member is rotated 10 degrees from the state of (D), and FIG. 6F is a diagram showing a state where the rotary cylinder member is rotated 10 degrees from the state of (E).

41 is an exploded perspective view showing a rotary cylinder member, a piston holding member, and a piston of a fluid rotary machine to which the second example of the back pressure relief means shown in FIG. 20 is applied.

FIG. 42 is a diagram showing the positional relationship between the center positions of the salient poles of the stator core of the generator and the magnetic poles of the magnet, and the cylinder chamber.

FIG. 43 is a plan view showing the first embodiment in which the rotary cylinder device of the present invention is configured as a rotary compressor, and in which the upper case and the piston holding member are removed.

FIG. 44 is a vertical sectional view of the rotary compressor shown in FIG. 43.

45 is an exploded perspective view of the rotary compressor of FIG. 43. FIG.

FIG. 46 is a schematic configuration diagram of a lubricating oil circulation mechanism.

47 is a bottom view of the rotary compressor of FIG. 43. FIG.

48 is a perspective view showing a bearing plate of the rotary compressor of FIG. 43. FIG.

FIG. 49 is a diagram showing the positional relationship between the suction port and the discharge port and the cylinder chamber where the piston is located at the outermost peripheral end of the cylinder chamber.

FIG. 50 is a plan view showing a second example of the back pressure relief means of the rotary compressor in a state in which the upper case and the piston holding member are removed from the rotary compressor.

51 is a sectional view of FIG. 50. FIG.

FIG. 52 is a view for explaining the operation of the rotary compressor in FIG. 43, and FIG. 52 (A) is a view showing a state in which one piston has crossed the cavity and the other piston has entered the deepest part of the cylinder chamber. , (B) is the rotary cylinder member 1 from the state of (A).
The figure which shows the state which rotated 5 degrees, (C) the figure which shows the state which rotated the rotating cylinder member 15 degrees from the state of (B),
(D) is a view showing a state where the rotary cylinder member is rotated 15 degrees from the state of (C), (E) is a view showing a state where the rotary cylinder member is rotated 15 degrees from the state of (D), (F) )
FIG. 11 is a diagram showing a state in which the rotary cylinder member is rotated 15 degrees from the state of (E).

FIG. 53 is a perspective view showing a modified example of the bearing plate.

FIG. 54 is a view for explaining the operation of another embodiment of the rotary compressor, (A) showing a state in which one of the three pistons has reached the deepest part of the cylinder chamber; (B)
Shows a state where the rotary cylinder member is rotated 10 degrees from the state of (A), (C) shows a state where the rotary cylinder member is rotated 10 degrees from the state of (B), and (D) shows ( The figure which shows the state which rotated the rotary cylinder member 10 degrees from the state of C), (E) shows the state which rotated the rotary cylinder member 10 degrees from the state of (D), (F) (E)
It is a figure which shows the state which rotated the rotating cylinder member from the state of 10 degree.

FIG. 55 is a plan view showing a third example of the back pressure relief means of the rotary compressor with the upper case and the piston holding member removed.

56 is a cross-sectional view of the rotary compressor of FIG. 55.

FIG. 57 is a conceptual diagram showing an example in which the cylinder chambers of the rotating cylinder member are not evenly distributed in the circumferential direction.

FIG. 58 is a conceptual diagram showing an example in which a cylinder chamber is formed by being offset.

FIG. 59 is a perspective view showing an example in which a magnet is arranged on the piston.

FIG. 60 is a perspective view showing another example in which a magnet is arranged on a piston.

FIG. 61 is a perspective view showing an example in which a magnet is arranged on a rotating cylinder member.

FIG. 62 is a perspective view showing another example in which magnets are arranged on a rotating cylinder member.

FIG. 63 is a conceptual diagram showing how a corner of a hollow portion of a rotary cylinder member is chamfered.

FIG. 64 is a cross-sectional view showing an example of a rotary cylinder member and a piston holding member in which a passage for releasing back pressure is formed.

65 is a perspective view showing the rotary cylinder member of FIG. 64. FIG.

66 shows the piston holding member of FIG. 64, (A) is a perspective view seen from the side opposite to the rotary cylinder member, and (B) is a perspective view seen from the rotary cylinder member side.

FIG. 67 is a cross-sectional view showing an example in which the rotary cylinder device of the present invention is used as a fluid power generator equipped with a rotation speed detecting means.

FIG. 68 is a cross-sectional view showing an example in which the rotary cylinder device of the present invention is used as a flow meter equipped with a rotation speed detecting means.

FIG. 69 is a cross-sectional view showing an example in which the rotary cylinder device of the present invention is a fluid pump provided with a rotation speed detecting means.

FIG. 70 is an exploded perspective view showing a conventional rotary cylinder device.

71 is a view for explaining the operation of the rotary cylinder device of FIG. 70, (A) showing a state in which two pistons have entered halfway into each of the two cylinder chambers;
In (B), the support member is moved counterclockwise from the state of (A) by 30
The state where the support member is rotated 30 degrees counterclockwise from the state of (B),
In (D), the support member moves counterclockwise from the state of (C) by 30
It is a figure which shows the state rotated once.

FIG. 72 is a perspective view showing an eighth example of a piston shape.

[Explanation of symbols]

1 Rotary type cylinder device 2 Rotating cylinder member 3,4 piston 5 Piston holding member 6 casing 61 entrance 62 exit O Rotational axis of rotating cylinder member 22,23 Cylinder chamber X Center of rotation of piston holding member

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F04C 18/54 F term (reference) 3H040 AA01 AA07 BB01 BB14 CC09 DD02 DD07 DD09 DD11 DD15 3H070 AA01 AA05 BB03 BB12 CC22 DD02 DD22 DD93

Claims (10)

[Claims] 1. A rotary cylinder member having a cylinder chamber formed so as to pass through a rotation shaft center and rotating about the rotation shaft center, a piston which makes a reciprocating linear motion by making surface contact in the cylinder chamber, and holding the piston. A piston holding member that rotates around a rotation center that is eccentric from the rotation axis of the rotating cylinder member, rotatably supports and accommodates the rotating cylinder member and the piston holding member, and at least one fluid inlet And a casing having at least one outlet for the fluid, wherein the piston is held rotatably at a position spaced from the center of rotation of the piston holding member by a certain distance. Rotary type cylinder device. 2. A guide portion that guides the piston in a sliding direction is formed in the cylinder chamber, and a guide engagement portion that engages with the guide portion is formed in the piston. The rotary cylinder device according to claim 1. 3. The inlet communicates with the cylinder chamber in the casing in either one of the regions divided by a line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. The outlet is provided so as to communicate with the cylinder chamber in the casing in any one of the other regions divided by a line connecting the rotation axis of the rotation cylinder member and the rotation center of the piston holding member. The rotary cylinder device according to claim 1 or 2, wherein 4. The rotary cylinder device according to claim 1, wherein a surface of the piston facing the piston holding member is a flat surface. 5. The cross-sectional shape of the piston and the cross-sectional shape of the cylinder chamber are similar shapes forming a slidable slight gap. Rotary cylinder device. 6. A magnetic fluid is disposed in a gap formed between the piston and the cylinder chamber, and a magnet for holding the magnetic fluid in the gap is provided at a contact portion between the piston and the cylinder chamber. The rotary cylinder device according to claim 1, wherein the rotary cylinder device is provided in the vicinity. 7. A plurality of the pistons and the cylinder chambers are formed, and the plurality of cylinder chambers are formed so as to intersect each other including the rotation axis of the rotary cylinder member. 7. The rotary cylinder device according to any one of 1 to 6. 8. The rotary cylinder device according to claim 7, wherein the cylinder chambers are arranged at positions equally distributed in the circumferential direction on the rotary cylinder member. 9. The rotary cylinder device according to claim 7, wherein the length of the portion where the plurality of cylinder chambers intersects in the moving direction of the piston is shorter than the length of the piston. 10. The chamfered portion is formed at a portion where the plurality of cylinder chambers intersect with each other.
10. The rotary cylinder device according to any one of 1 to 9.