JP2003074465A - Rotary cylinder device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent leakage of a fluid from a part between a piston and cylinder member, and to reduce loss of driving force of the cylinder member due to back pressure fluid entering the back of the cylinder member. SOLUTION: This rotary cylinder device is provided with a rotary cylinder member 2, pistons 3, 4, a piston holding member 5, a casing 6, a cylinder supporting plate 71 interposed between the casing 6 and the rotary cylinder member 2 to rotatably support the rotary cylinder member 2, a back pressure fluid recess 63 provided in the inner peripheral surface of the casing 6 to communicate a clearance gap C between the cylinder support plate 71 and the rotary cylinder member 2 with a cylinder chamber 22, and a back pressure fluid passing groove 71a provided in the cylinder support plate 71 to communicate with the back pressure fluid recess 63. The back pressure fluid is guided into the cylinder chamber prior to a compression stroke.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary cylinder device.

[0002]

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. 27 and 28, a rotary cylinder device disclosed in Japanese Patent Laid-Open No. 56-118501 discloses a circular cylinder member 102 fixed to 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 are moved to the positions shown in FIGS.
As shown in FIG. 28D, 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.

[0007]

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 a structure in which there is a margin in the width direction when entering each of the cylinder chambers 105a to 105f 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 No. 57-87184 and Japanese Utility Model Laid-Open No. 58-92486 are arranged in a basic configuration, that is, radially while rotating pistons radially arranged. 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.

On the other hand, even if the contact area between the piston and the inner wall of the cylinder chamber is increased to improve the sealing performance, it is desired to reduce energy loss due to an increase in frictional resistance and wear of the sliding portion. There is also a request.

Further, when the wear is reduced,
A small clearance (gap) between the cylinder member and the inner surface of the casing is filled with lubricating liquid and sealed so that fluid cannot flow between the front surface side and the back surface side of the cylinder member. When the above gas is compressed, the high pressure gas may leak from the sealing surface to the back side of the cylinder member together with the lubricating liquid. In such a case, a pressure (back pressure) that presses the cylinder member in the thrust direction is generated by the submerged fluid, and there is a problem that the resistance increases and the loss of the driving force increases, and the wear is accelerated. May occur.

An object of the present invention is to prevent fluid from leaking between a piston and a cylinder member, so that rotary motion can be converted into fluid energy with low loss, and frictional resistance between the piston and the cylinder member can be reduced. It is to provide a rotary type cylinder device that can be reduced. Further, an object of the present invention is to provide a rotary cylinder device capable of reducing the loss of the driving force of the cylinder member due to the back pressure fluid leaking from the high pressure cylinder chamber and sneaking into the back of the cylinder member. Especially.

[0013]

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; A casing that rotatably supports and accommodates at least one fluid inlet and at least one fluid outlet, and rotation of the casing so that the gap between the casing and the rotating cylinder member communicates with the cylinder chamber. A back pressure fluid escape provided on the inner peripheral surface in contact with the cylinder member, and the piston is a piston holding member. It is held rotatably at a certain distance from the center of rotation and rotatably around that position, and the back pressure fluid that leaks from the cylinder chamber at high pressure and spills into the gap is released by back pressure fluid before the compression stroke. The feature is that it is guided into the cylinder chamber.

According to another aspect of the present invention, in the rotary type cylinder device, a cylinder chamber is formed so as to pass through the rotary shaft center, and a rotary cylinder member that rotates around the rotary shaft center is in surface contact with the rotary cylinder member to make a reciprocating straight line. A moving piston, and a piston holding member that holds the piston and rotates about a rotation center that is eccentric from the rotation axis of the rotating cylinder member,
A casing that rotatably supports and accommodates the rotating cylinder member and the piston holding member, and has a casing having at least one fluid inlet and at least one fluid outlet, and a rotating cylinder interposed between the casing and the rotating cylinder member. A cylinder support plate that rotatably supports the member,
A back pressure fluid relief provided on an inner peripheral surface of the casing that contacts the rotation cylinder member so as to communicate the gap between the cylinder support plate and the rotation cylinder member with the cylinder chamber, and communicates with the back pressure fluid relief. And a back pressure fluid passage groove provided on the cylinder support plate, the piston is held at a position a certain distance from the center of rotation of the piston holding member and is rotatable about that position, and the cylinder is The back pressure fluid that leaks from the chamber at high pressure and spills into the gap is guided into the cylinder chamber before the compression stroke by the back pressure fluid escape and back pressure fluid passage grooves.

Therefore, in these rotary type cylinder devices, when rotation is externally input to the rotary cylinder member or the piston holding member, the rotation of the rotary cylinder member and the piston holding member causes the piston to rotate about the center of rotation. However, the piston reciprocates in the cylinder chamber by rotating (revolving) about the rotation center of the piston holding member.

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 and liquidity are high. The denseness can be increased.

Moreover, in these rotary type cylinder devices, the high pressure back pressure fluid leaking from the high pressure cylinder chamber and sneaking into the gap on the back side of the rotating cylinder member is released by the back pressure fluid communicating with the gap. It can be guided to the low pressure part of the front side cylinder chamber. In this case, the back pressure that tries to press the rotary cylinder in the thrust direction is reduced, and the loss of the driving force of the rotary cylinder member is reduced.

Further, in the rotary cylinder device according to the second aspect of the present invention, a back pressure fluid passage groove communicating with the back pressure fluid escape is provided in the cylinder support plate interposed between the rotary cylinder member and the casing. Therefore, the back pressure fluid that has sunk into the gap on the back side of the rotary cylinder member can be guided to the low pressure portion of the cylinder chamber by passing through the back pressure fluid passage groove and the back pressure fluid escape.

According to another aspect of the rotary cylinder device of the present invention, the back pressure fluid passage groove is provided with a circular step portion provided on an outer edge of the cylinder support plate. In this case, the back pressure fluid can be guided to the back pressure fluid relief and guided to the low pressure portion of the cylinder chamber.

Further, in the rotary cylinder device according to the fourth aspect, the back pressure fluid passage groove is provided with a plurality of grooves radially provided on the surface of the cylinder support plate on the rotary cylinder member side. In this case, even if the back pressure fluid is submerged in the gap, the back pressure fluid can be guided from the gap by passing through any of these grooves. Further, when such a plurality of grooves are provided, it is easy to allow the back pressure fluid to escape even when there is a large amount of back pressure fluid.

According to another aspect of the rotary cylinder device of the present invention, a concave fluid reservoir is formed at the center of the surface of the cylinder support plate on the side of the rotary cylinder member. In this case, incompressible excess lubricating liquid can be stored in this fluid reservoir in the process of guiding the back pressure fluid from the gap.

In the rotary type cylinder device according to the sixth aspect, a plurality of pistons and 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. In this case, a rotary cylinder device that is rotated by a plurality of pistons is provided.

[0024]

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.

1 to 4 show a first embodiment of a rotary type cylinder device of the present invention. In the present embodiment, the rotary cylinder device that pressurizes gas as the fluid has been described, but the fluid to pressurize is not limited to gas, and may be liquid or the like.

The rotary cylinder device 1 has a plurality of cylinder chambers 22 and 23 arranged radially and passing through the rotation axis O, and a rotation cylinder member 2 which rotates about the rotation axis O, and the cylinder chambers 22 and 23. Pistons 3 and 4 that reciprocate linearly in surface contact with each other, a piston holding member 5 that holds the pistons 3 and 4 and rotates about a rotation center that is eccentric from the rotation axis O of the rotation cylinder member 2, and a rotation cylinder Between the casing 6 that rotatably supports and accommodates the member 2 and the piston holding member 5 and that has at least one fluid inlet 61 and at least one fluid outlet 62, and between the casing 6 and the rotary cylinder member 2. Between the cylinder support plate 71 and the rotary cylinder member 2 for rotatably supporting the rotary cylinder member 2 A back pressure fluid relief 63 provided on the inner peripheral surface of the casing 6 that contacts the rotating cylinder member 2 so as to communicate the clearance C with the cylinder chambers 22 and 23, and a cylinder to communicate with the back pressure fluid relief 63. A back pressure fluid passage groove 71 a provided in the support plate 71 is provided. In the present embodiment, the rotary cylinder member 2 employs the cylinder chambers 22 and 23 and the pistons 3 and 4, but the invention is not limited to this, and it is sufficient to have at least one cylinder chamber and piston.

The rotary cylinder member 2 is formed in a disk shape having a predetermined thickness, and is rotatably arranged in the internal space of the casing 6. Support shaft 2 for casing 6
1 is press-fitted and fixed, and the rotary cylinder member 2 is a support shaft 2
1 is rotatably supported. A cylinder support plate 7 is provided between the rotary cylinder member 2 and the casing 6.
1 is provided. The cylinder support plate 71 receives the load in the thrust direction acting on the rotary cylinder member 2 and supports the rotary cylinder member 2, and the balls 72
And a retainer (provided between the rotary cylinder member 2 and the cylinder support plate 71, but not shown in the present specification) form a ball bearing that supports the load in the thrust direction applied to the rotary cylinder member 2. Therefore, the rotary cylinder member 2 is rotatable within the casing 6 about the support shaft 21 as a rotation center.

The piston holding member 5 of the rotary cylinder member 2
A space formed by a cross-shaped groove formed by using the four fan-shaped base portions 25 is provided on the side surface. This cross-shaped space has four cylinder parts 22a, 22b, 23.
It is composed of a and 23b and a portion (hereinafter referred to as a cavity) 24 where these intersect. That is, on the surface of the rotary cylinder member 2 on the piston holding member 5 side, the rotation axis O
A cavity 24 having a predetermined area and having a bottom surface is formed. Then, four cylinder portions 22a, 22b, 23a, 23b having a rectangular cross section are provided radially around the rotation axis O in the hollow portion 24. Cylinder parts 22a, 22b, 23a, 23b
Has an open top surface, and the other three surfaces are all flat. The first cylinder portion 22a, the hollow portion 24, and the second cylinder portion 22b form the cylinder chamber 22, and the third cylinder portion 23a, the hollow portion 24, and the fourth cylinder portion 23b form the cylinder chamber 23, respectively. ing. As is clear from FIG. 14, the cylinder chambers 22 and 23 have the rotational axis O of the rotary cylinder member 2.
Are formed so as to intersect with each other and are arranged at positions equally distributed in the circumferential direction.

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:
They are formed so as to be flat with each other, and they are provided so as to slide on each other.

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 fluid inlet (hereinafter referred to as “suction port”) 61 and a fluid outlet (hereinafter referred to as “discharge port”) 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 piston holding member 5 is formed in a disk shape having an outer diameter smaller than the outer diameter of the rotary cylinder member 2, and is housed in a case cover 74 which covers the casing 6. A support plate 78 is provided between the case cover 74 and the piston holding member 5. The support plate 78 receives a load in the thrust direction acting on the piston holding member 5, and supports the load in the thrust direction applied to the piston holding member 5. Although not particularly shown, the piston holding member 5 may be rotatable within the case cover 74, and a ball bearing may be configured by combining a ball and a retainer.

The rotation center position X of this piston holding member 5
At one end, one end of the input 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 tip end side of the input shaft 51 penetrates a hole 75 a provided in the cap 75 and projects to the outside. 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 input 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 input shaft 51 is fixed. It is fixed upright. And the support shaft 5
Pistons 3 and 4 are rotatably fitted in the gears 2 and 53.

The pistons 3, 4 are, as shown in FIGS. 5 and 6, front and rear surfaces 31, 31, 4 during reciprocating linear motion.
1, 41 are formed to have a slight roundness,
The other four surfaces, that is, the upper surfaces 32 and 42, the bottom surfaces 33 and 43, and the side surfaces 34, 34, 44, and 44, which are fitted in the cylinder chambers 22 and 23, are formed into flat surfaces. That is, the pistons 3 and 4 have a substantially rectangular block shape. Then, among the surfaces formed on the flat surfaces of the pistons 3 and 4, the bottom surface 33 excluding the upper surfaces 32 and 42,
43 and the both side surfaces 34, 34, 44, 44,
It becomes a sliding surface with the cylinder chambers 22 and 23 when it is fitted into the cylinders 2 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, 4
A may be a through hole.

As shown in FIGS. 4 to 10, a large number of dimples 29 are provided on the sliding portions of the rotary cylinder member 2, the pistons 3, 4, and the piston holding member 5 (dimples are shown in other drawings. 29 is omitted). That is,
The rotating cylinder member 2 rotates while sliding with respect to the casing 6, the piston holding member 5, and the retainer, and the piston holding member 5 is rotated by the case cover 74 and the rotating cylinder member 2.
The pistons 3 and 4 make a reciprocating linear motion while sliding with respect to the rotating cylinder member 2 and rotate while sliding with respect to the piston holding member 5.

A large number of dimples 29 are provided on at least one of the sliding facing surfaces. In this embodiment, a surface of the rotary cylinder member 2 that slides on the casing 6, the piston holding member 5, and the retainer,
A large number of dimples 29 are formed on the surface of the piston holding member 5 that slides on the case cover 74 and on the surface of the pistons 3 and 4 that slides on the rotary cylinder member 2 and the piston holding member 5.

The dimple 29 has a hemispherical shape, for example, as shown in FIG. Dimple 29
Is formed to have a size capable of forming an oil film on the sliding surface to prevent fluid leakage and holding a sufficient amount of lubricant to reduce frictional resistance. For example, the diameter is 0.3
It is preferable that the dimple 29 has a size of about 3 mm and a depth of about 0.05 mm.

FIG. 12 shows the relationship between the piston holding member 5 and the loci of the pistons 3 and 4 during rotation. The radius R1 of the piston holding member 5, a distance R2 that is 1/2 the distance between the support shafts 52 and 53, and the radius R of the outermost diameter locus when the pistons 3 and 4 rotate.
The relationship of 3 is R1> (R2 + R3), and the radius difference ΔR occurs. If the radius R1 is smaller than the distance R2 + the radius R3, the locus of the outermost diameter of the piston jumps out from the piston holding member 5 during operation, and the piston 3,
In order to secure the rotation stability and the hermeticity of No. 4, it is necessary to improve the processing accuracy of the parts. On the other hand, by setting the relationship of radius R1> distance R2 + radius R3 as described above, it is possible to secure the stability of rotation of the pistons 3 and 4 and the hermeticity without making the machining accuracy of the parts so severe. It will be easier. However, this relationship is for ensuring the airtightness, etc., and is not limited to this relationship, and the radius R
It is needless to say that 1 may be substantially equal to or smaller than the distance R2 + radius R3.

The suction port 61 has a shallow recess 61a formed in the inner peripheral surface of the casing 6, a communication hole 61b for communicating the recess 61a with the outside of the casing 6, and the communication hole 61b on the outer surface side of the casing 6. Intake pipe 61 connected to
and c. Then, when the rotary cylinder member 2 rotates, the recess 61a is provided in each of the cylinder portions 22a to 22a.
23b, respectively.

Further, the discharge port 62 is the recess 6 of the suction port 61.
1a and a shallow recess 62a, and this recess 62a
And a communication hole 62b that communicates with the outside of the casing 6,
The communication hole 62b is composed of an exhaust pipe 62c connected to the outer surface side of the casing 6. And the recess 62
When the rotating cylinder member 2 rotates, a is connected to each of the cylinder parts 22a to 23b.
The recess 61a and the recess 62a are arranged so as to improve the efficiency of the device.

Next, a mechanism for effectively guiding the back pressure fluid that has sunk into the gap C between the cylinder support plate 71 and the rotary cylinder member 2 to the cylinder chambers 22 and 23 will be described. The back pressure fluid as referred to in this specification is a fluid such as a gas such as air or a liquid such as a lubricating liquid, and is a peripheral surface of the rotary cylinder member 2 when it is compressed in the cylinder chambers 22 and 23 to have a high pressure. It refers to the material that has leaked from the seal portion between the inner peripheral surface of the casing 6 and sunk into the gap C.

As shown in FIG. 1, the casing 6 is a member in which the rotary cylinder member 2 is housed, and a support shaft 21 for rotatably supporting the rotary cylinder member 2 is fixed. The casing 6 is provided with a back pressure fluid relief 63 on its inner peripheral surface as shown in FIGS.

The back pressure fluid escape 63 compresses the back pressure fluid leaking from the compressed and high pressure cylinder chambers 22 and 23 into the backside clearance C of the rotary cylinder member 2 in the cylinder chamber 22 (or 23). Cylinder part 22a (or 22b, 23a, 2 which is at low pressure before the stroke)
3b) is a flow path for reducing the back pressure by guiding it, and has a shape and installation position suitable for guiding the back pressure fluid. For example, the back pressure fluid relief 63 of this embodiment is shown in FIG.
As shown in FIG. 2, the rear surface side area (gap C) and the front surface side area (cylinder chamber 22, of the rotary cylinder member 2 partitioned by the rotary cylinder member 2 and the cylinder support plate 71).
23) is formed of a shallow groove provided on the inner peripheral surface of the casing so as to communicate with the casing 23, and the back pressure fluid that has sunk into the gap C has a low pressure in the cylinder portion 22a (or 22b, 23a, 23).
b) (see FIG. 14 etc.). The back pressure fluid escape 63 is not limited to such a groove, but may be a flow path configured to communicate both regions with each other, for example, by a through hole penetrating the inside of the casing 6.

Further, the suitable groove width and circumferential position of the back pressure fluid escape 63 are, for example, separated from the suction port 61 and start communicating with the cylinder portion 22b which is further rotated a little from that (FIGS. 14 and 15). The width and position are such that the cylinder portion 23a, which is 90 degrees ahead of the portion 22b, continues to communicate with the cylinder portion 22b until just before the cylinder portion 23a is ventilated to the discharge port 62. However, the communication timing is not particularly limited to such timing, and the cylinder chamber 2
It can be appropriately changed according to the size and position of 2, 23, the rotation speed, and the like.

Further, the cylinder support plate 71 in the rotary cylinder device 1 of the present embodiment is provided with a screw 69 which penetrates the cylinder support plate 71 from the rotary cylinder member 2 side and is screwed into the casing 6 as shown in FIG. It is screwed into the casing 6 so that it cannot rotate. In addition, as shown in FIG.
Is connected to the above-mentioned back pressure fluid relief 63 and this relief 63
A back pressure fluid passage groove 71a for guiding the back pressure fluid is provided therein. The back pressure fluid passage groove 71a is, for example, as shown in FIG. 3, a plurality of radial radial grooves 71b extending from the center of the plate to the outer circumference, and a circular outer peripheral edge of the plate that connects the outer peripheral side end portions of the radial grooves 71b. And a step 71c.
The radial groove 71b is preferably radial as described above in terms of plate manufacturing, passage of fluid, and the like, but is not particularly limited thereto, and the gap C and the back pressure fluid relief 63 communicate with each other. For example, a plurality of grooves provided obliquely like teeth of a helical gear may be used as long as they can be formed.

A fluid reservoir 71d is formed at the center of the surface of the cylinder support plate 71 on the rotary cylinder member 2 side. The fluid reservoir 71d is a space that allows temporary storage of fluid, particularly incompressible liquid, and retains incompressible excess lubricating liquid in the process of guiding the back pressure fluid from the gap C. Can be kept. In the case of the present embodiment, the fluid reservoir 71d is a disk-shaped space as shown in FIG. 3, but the shape and depth are not particularly limited.

Further, as shown in FIG. 3, among the plurality of radial grooves 71b, the groove (indicated by reference numeral 71e) which is continuous with the back pressure fluid escape 63 of the casing 6 is preferably wider than the other grooves 71b. In such a case, the other radial groove 71b
Since the back pressure fluid that has once passed through and collected in the fluid reservoir 71d easily escapes to the back pressure fluid escape 63 through the wide groove 71e, the smooth circulation of the back pressure fluid can be secured.

Further, the rotary cylinder device 1 is provided with a lubricant circulating mechanism 15. This lubricant circulation mechanism 15
Is, for example, as shown in FIG.
A lubricant inflow passage 17 that communicates with the rear surface of the rotary cylinder member 2 and guides the lubricant from the lubricant tank 16 into the casing 6 and a rear surface side of the piston holding member 5 communicate with the lubricant tank 16. Is provided with a lubricant outflow passage 18 for guiding. In the middle of the lubricant inflow passage 17,
A filter (not shown) is provided. The lubricant may be any lubricant having lubricity such as lubricating oil, lubricating grease, water, gas and other fluids, and may be a working fluid (non-compressed fluid) of the apparatus.

The lubricant inflow passage 17 has a case cover 74.
Is connected to the port 19 provided in the. The lubricant introduced from the port 19 into the casing 6 propagates through the gaps between the members in the casing 6 and lubricates the sliding surface.
Then, it flows out from the port 20 provided in the casing 6 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 → the inside of the casing 6 → the lubricant outflow passage 18 → the lubricant tank 16 Circulates to.

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. 14 to 19. 14 to 19, the piston 4 is shaded so that the movements of the pistons 3 and 4 can be easily understood.

In FIG. 14, the piston 3 which 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
Are cylinder parts 22a, 22 on both sides of the cavity 24.
The cylinder part 2
Both 2a and 22b are in a state of being filled with the fluid taken in through the suction port 61.

In the state shown in FIG. 14, the cylinder portion 2
The outermost peripheral end of 2a is in a state immediately before communicating with the recess 62a of the discharge port 62, and the cylinder portion 22a is in a state immediately before communicating with the exhaust pipe 62c via the recess 62a. Further, the outermost peripheral end portion of the cylinder portion 22b is in a state immediately after the communication state with the recess 61a of the suction port 61 is completed, and the cylinder portion 22b has the recess 6a.
The communication with the intake pipe 61c via 1a is terminated. 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 which 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 recess 62a of the discharge port 62.

When the piston holding member 5 is rotated clockwise (direction indicated by an arrow A) from the state shown in FIG. 14 by a motor drive or the like, the pistons 3 and 4 move in the direction indicated by an 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 arrow B direction (clockwise direction) is applied to the rotary cylinder member 2, and the rotary cylinder 2 rotates in the arrow B 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 about the rotational center position X is the rotational speed about the rotational axis O of the rotating 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 a circle whose radius is the length from the rotation axis O of the rotary cylinder member 2 to the center of the rotation center position X2 in FIG.

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 of FIG. 14, the piston holding member 5 is
FIG. 15 shows a state in which the cylinder member 2 is rotated by 0 degrees and the cylinder member 2 is rotated by 30 degrees.

That is, by the above-described operation from FIG. 14 to FIG. 15, 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. At the time of this movement, since the piston 3 and the cylinder portion 22a face each other in plane,
Since the lubricant is held by a large number of dimples 29 formed on the sliding surface, the fluid hardly leaks from the contact surfaces. By this operation, the fluid in the cylinder portion 22a is discharged through the recess 62a into the discharge pipe 62.
Efficiently discharged to c. Since the distance in the longitudinal direction of the cylinder chamber 22a is shorter than twice the total length of the piston 3, it has advanced by about 1/2, but the rear end portion of the piston 3 is still the hollow portion 24. It remains in the inside.

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 hollow portion 24 side by about 1 /.
Move about 9. At the time of this movement, since the piston 4 and the cylinder portion 23b are in contact with each other on their flat surfaces,
Many dimples 29 formed on the sliding surface of the piston 4
Since the lubricant is held by, the fluid hardly leaks 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. 16 shows a state in which the piston holding member 5 further rotates 60 degrees from the state shown in FIG. 15, and thereby the cylinder member 2 further rotates 30 degrees.

That is, by the operation from FIG. 15 to FIG. 16 described above, the piston 3 advances further into the inside of the cylinder part 22a from a position of about 1/2, more specifically about 8/9. Move to the position. 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 hollow 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. 17 shows a state in which the piston holding member 5 further rotates 60 degrees from the state shown in FIG. 16, and thereby the cylinder member 2 further rotates 30 degrees.

That is, by the above-described operation from FIG. 16 to FIG. 17, the piston 3 moves further toward the inner side from the position where it has entered the inside of the cylinder portion 22a by about 8/9, specifically, the outermost periphery of the cylinder portion 22a. Move to the end. By this operation, the fluid remaining in the cylinder portion 22a is
Further, it 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. 14, the cylinder portion 22a is in a state in which 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 in a state immediately before communicating with the recess 62a of the discharge port 62, and the cylinder chamber 23a is immediately communicating with the exhaust pipe 62c through the recess 62a. It is in the state of. Further, the outermost peripheral end of the cylinder portion 23b is in a state immediately after the communication state with the recess 61a of the suction port 61 is finished, and the cylinder portion 22b is in a state in which 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 where the positions of the pistons 3 and 4 are exchanged with each other in the state of FIG. 11 described above. That is, in the pistons 3 and 4, the piston holding member 5 rotates 180 degrees and the rotary cylinder member 2 simultaneously rotates 90 degrees, so that the cylinder parts 22a to 23 are rotated.
The positions of one of the cylinders b are moved in and out, and the positions of the cylinders are switched. And
The rotary type cylinder device 1 of the present embodiment is configured to perform suction, pressurization or compression, and conveyance operations by repeating this operation. That is, the pistons 3 and 4 are
When the piston holding member 5 further rotates 180 degrees, that is, 360 degrees from the initial point, it returns to the initial position shown in FIG. On the other hand, the rotary cylinder member 2 is 180
Rotate once.

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.

Next, the operation of guiding the back pressure fluid to the constant pressure portions of the cylinder chambers 22 and 23 by the back pressure fluid relief 63 and the like will be described.

In the rotary cylinder device 1 configured as described above, the rotational force input from the input shaft 51 is transmitted to the piston holding member 5, and the piston holding member 5
When the rotary motion of the motor is performed at a constant angular velocity, the pistons 3 and 4 perform a rotary motion at a constant angular velocity around the rotation center position X, and the rotary cylinder member 2 also performs a constant angular velocity motion with this motion ( 14 to 19). This operation pressurizes, sucks, and conveys the fluid.

As shown in FIG. 15, when the cylinder chamber 23 and the suction port 61 have started to communicate with each other, the piston 4 moves along the cylinder chamber 23 in the direction of the arrow D, and the casing 6 is provided accordingly. The fluid is sucked into the cylinder portion 23b from the suction port 61. The fluid suction continues as the rotary cylinder member 2 rotates until the state shown in FIG. 17, that is, the state immediately before the communication between the cylinder chamber 23 and the suction port 61 is interrupted.

In the state shown in FIGS. 17 to 19, the fluid in the cylinder portion 23a of the cylinder chamber 23 is compressed, and the cylinder chamber 23 communicates with the discharge port 62 provided in the casing 6 as the rotary cylinder member 2 rotates. The compressed gas is discharged from there together with the lubricating liquid. At this time,
A part of the fluid leaked from between the rotary cylinder member 2 and the casing 6 may sneak into the back side of the rotary cylinder member 2, but the spilled fluid may be the cylinder support plate 71.
It goes around in the circumferential direction through a circular stepped portion 71c provided around the circumference of the fluid, or through a radial groove 71b, and a fluid reservoir 7 in the central portion.
1d, through the wide groove 71e, through the back pressure fluid escape 63 of the casing 6, and through the low pressure side cylinder portion 22a (or 22b, 23a, of the cylinder chambers 22, 23).
23b).

In this way, the fluid leaked to the back side of the rotary cylinder member 2 is rotated around the circular step portion 7 of the cylinder support plate 71.
1c, the radial groove 71b, and the wide groove 71e to pass through the back pressure fluid relief 63 of the casing 6 and the cylinder chambers 22 and 23.
Cylinder part 22 where the pressure is lower than the discharge side of
Since it is guided to a (or 22b, 23a, 23b), it does not accumulate in the gap C and become a high pressure so as to push up the rotary cylinder member 2 in the thrust direction. Friction resistance generated when pressed against 74 is reduced.

During this operation, each piston 3,
4 will face each cylinder part 22a-23b by the planes with a large sliding area. In addition, a lubricant is stored in each of the many dimples 29 formed on the sliding surface of each piston 3, 4, and each piston 3, 4
With the reciprocating linear motion of the above, the lubricant fills the gaps between the pistons 3 and 4 and the cylinder portions 22a to 23b. For these reasons, it is possible to prevent fluid from leaking from the gaps between the pistons 3 and 4 and the cylinder portions 22a to 23b.

That is, in addition to the sliding surfaces of the pistons 3 and 4 being in surface contact with each other, the lubricant is supplied from the dimples 29 to the gaps, so that the lubricant film can be prevented from being cut off. Even if the fluid enters the gap, it stays in the dimples 29, so that it is difficult to pass through the gap. For these reasons, the sealing property is improved.

Further, by supplying the lubricant to the gap from the dimples 29, it is possible to prevent the lubricant film from being broken, so that a good lubrication state is maintained, the sliding resistance is reduced, and the wear is suppressed. be able to. This is
Not only the gaps between the pistons 3 and 4 and the cylinder parts 22a to 23b, but also the gap between the rotary cylinder member 2 and the casing 6, the gap between the piston holding member 5 and the case cover 74, the pistons 3 and 4 and the rotary cylinder. The same applies to the sliding surfaces of the rotary cylinder member 2, the pistons 3, 4, and the piston holding member 5, such as the gap between the member 2 or the piston holding member 5.

Furthermore, in addition to improving the sealing performance of the pistons 3 and 4, and reducing the frictional resistance of each sliding surface,
Since the dimples 29 are formed on the sliding surface, the sliding area is reduced by that much, and the sliding resistance can be reduced, so that mechanical loss is reduced and mechanical efficiency is improved. it can.

Since the rotary cylinder member 2 is supported by the support shaft 21 fixed to the casing 6, the clearance between the inner peripheral surface of the casing 6 and the outer peripheral surface of the rotary cylinder member 2 can always be kept constant. it can. Therefore, it is possible to prevent the contact between the rotary cylinder member 2 and the casing 6 and use a low-viscosity lubricant, and to suppress the power loss accordingly.

In the rotary type cylinder device 1 of the first embodiment described above, the number of cylinder chambers is two (4 cylinder portions) and the number of pistons is two. The number may be one. Also, FIG.
The number of cylinder chambers and the number of pistons may be three as in the second and third embodiments shown in FIG.

A rotary type cylinder device 1 shown in FIG. 20 as a second embodiment of the present invention has six cylinder parts 22a in a casing 6, similar to the rotary cylinder device 1 of the first embodiment described above. 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.
Further, similarly to the rotary cylinder device 1 of the above-described embodiment, each piston 3 of the rotary cylinder device 1 is
Dimples 29 are also formed on the rotary cylinder members 2, 4, and the piston holding member 5, respectively.

In the rotary type cylinder device 1 constructed as described above, when the pistons 3, 4, 9 rotate in the direction of the arrow A'by the rotation of the piston holding member, the rotary cylinder member 2 moves in the direction of the arrow along 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 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 dimensions of the pistons 3, 4, 9 are such that they can engage with both 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. Be sure to get in and out of the
Pressurization, compression, and conveyance operations are performed.

Further, FIG. 2 shows a third embodiment of the present invention.
The rotary type cylinder device 1 shown in FIG. 1 has six cylinder parts 22a, 22b, 23a, 23b, 28a, 2 in the casing 6 as in the first and second embodiments.
A rotary cylinder member 2 having 8b and six fan-shaped bases 25 is rotatably arranged, and a piston holding member (not shown) is rotatably arranged at an eccentric position of the rotary cylinder member 2. . 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 20, the rotation ratio of both members arranged in the casing 6 of the rotary cylinder device 1 is such that the number of rotations 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. Further, similar to the rotary type cylinder device 1 of the embodiment of FIGS. 1 and 20, dimples 29 are formed on the pistons 3, 4, 9 of the rotary type cylinder device 1, the rotary cylinder member 2, and the piston holding member 5, respectively. Has been done.

In the rotary type cylinder device 1 thus constructed, when the pistons 3, 4 and 9 rotate in the direction of arrow A "by 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 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 with 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. 21, each piston 3, 4, 9 is composed of a substantially cubic block, and when it crosses the cavity / passage 241, it is separated 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.

The rotary type cylinder device 1 of the type having six cylinder chambers and three pistons as shown in FIGS. 20 and 21 has a balanced intake / exhaust and a small torque fluctuation.

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, but these recesses 61a,
The width of 62a can be arbitrarily set according to the application. For example, when a higher compression ratio is applied, 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 the positions facing the outer peripheral surface of the rotary cylinder member 2 of the casing 6, respectively. However, the suction port 61 and the discharge port 62 are
It may be provided on both sides in the vertical direction or on one side.

In each of the above embodiments, the piston holding members 5 and 90 are driven, but the rotating cylinder member 2 side may be driven.

The rotary cylinder device 1 can be used as a compressor of a cooling circuit composed of, for example, an evaporator, a condenser, a capillary tube, a radiating pipe and the like. That is, it can be used to compress and circulate the heat-exchanged refrigerant. Further, a motor for rotating the input shaft 51 may be housed in the casing 6.

A plurality of rotary cylinder devices 1 may be combined to form a multi-stage type. For example, when the rotary cylinder device 1 is a compressor, the fluid compressed by the compressor 1 is caused to flow into the compressor 1 of the next stage,
Higher pressure fluid can be obtained.

The above 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 scope of the present invention.
For example, the back pressure fluid relief 63 in the above-described embodiment is provided on a part of the inner peripheral surface of the casing 6 as shown in FIGS. 1 and 14, but the back pressure fluid relief 63 is provided in the cylinder chambers 22, 23. The shape and size are not particularly limited as long as they can communicate with the clearance C and guide the back pressure fluid, and can be appropriately changed. For example, FIGS.
As shown in FIG. 5, the back pressure fluid escape 63 is extended so as to reach the upper edge of the inner peripheral surface of the casing 6 so that the circulation of the back pressure fluid and the ease of manufacturing the groove can be simultaneously improved. Good.

In the above-described embodiment, the cylinder support plate 7 is provided between the rotary cylinder member 2 and the casing 6.
The rotary cylinder device 1 having the above-mentioned 1 has been described. The cylinder support plate 71 is preferable in that it facilitates the rotational movement of the rotary cylinder member 2, but the cylinder support plate 71 is not always necessary depending on the configuration of the rotary cylinder device 1, and the rotary cylinder is formed at the bottom of the casing 6. The member 2 may be directly received, but the configuration of the present invention in which the back pressure fluid is guided to the cylinder chambers 22 and 23 side is also applicable to such a rotary cylinder device 1. Specifically, by providing the back pressure fluid relief 63 on the inner peripheral surface of the casing 6, the back pressure fluid that has sunk into the gap C between the cylinder support plate 71 and the rotating cylinder member 2 as in the present embodiment. Can be guided to the cylinder chambers 22 and 23 side.

Although not shown in particular, instead of the back pressure fluid passage groove 71a provided on the cylinder support plate 71, a groove is provided at a position corresponding to the back pressure fluid escape 63 of the casing 6 on the outer peripheral portion of the rotary cylinder member 2. The back pressure fluid may be guided to the back pressure fluid escape 63 through this groove.

Further, in addition to the back pressure fluid relief 63 provided on the inner peripheral surface of the casing 6, a groove running in the circumferential direction or a groove running obliquely so as to intersect with the back pressure fluid relief 63 is provided on the inner peripheral surface of the casing 6. The back pressure fluid may be guided to the back pressure fluid escape 63 and guided to the low pressure side portions of the cylinder chambers 22 and 23 by passing through these grooves.

Further, in this embodiment, the cylinder support plate 71, the balls 72 and the retainer are provided to form the bearing, but the rotary cylinder device in which the bearing is omitted by directly receiving the rotary cylinder member 2 by the cylinder support plate 71. Also in 1, the mechanism for guiding the back pressure fluid to the low pressure side portion in the cylinder chambers 22 and 23 can be applied.

Further, the cylinder portion is replaced by the rotary cylinder member 2
It is not necessary to evenly distribute each other in the circumferential direction with respect to the cylinder parts 22a, 22b, 2 as shown in FIG.
3a and 23b do not have to be equally distributed in the circumferential direction with respect to the rotary cylinder member 2.

Further, as shown in FIG. 25, 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, for example, as shown in FIG. 26, 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. 26 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. This is important in a rotary cylinder device, in which not only the residual fluid reduces the efficiency of the compressor, but also the residual fluid in the compressed state expands rapidly due to the intake port, causing noise and vibration. Will cause to occur. 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 moving the piston smoothly.

The rotary cylinder member 2, the piston 3,
4. The shape of the dimple 29 formed on the sliding surface of the piston holding member 5 is not limited to the spherical shape shown in FIG. 11 (A), and may be, for example, a cylindrical shape shown in FIG. 11 (B). The conical shape shown in C) may be used.

[0106]

As described above, according to the rotary cylinder device of the first aspect, the contact area between the piston and the cylinder chamber can be made large, and the contact surface is formed by so-called line contact. The fluid resistance at the contact surface is greater than that of the conventional one, and the airtightness and liquidtightness can be improved. Therefore, it is possible to prevent the fluid from leaking between the piston and the cylinder member, convert the rotational motion into fluid energy with low loss, and reduce the frictional resistance between the piston and the cylinder member.

Moreover, according to this rotary type cylinder device, the high pressure back pressure fluid leaking from the high pressure cylinder chamber and sunk into the gap between the rotating cylinder member and the casing is
The back pressure fluid relief communicating with this gap can guide the fluid to the low pressure side portion of the cylinder chamber on the front side of the rotary cylinder member. In this case, since the high-pressure back pressure fluid can be collected in the cylinder chamber before compression, the back pressure can be effectively used. Further, since the back pressure that tries to press the rotary cylinder in the thrust direction escapes and decreases, it is possible to reduce the loss of the driving force of the rotary cylinder member and improve the operating efficiency.

Further, according to the rotary type cylinder device of the second aspect, since the back pressure fluid passage groove communicating with the back pressure fluid escape is provided in the cylinder support plate, the cylinder support plate is provided in the device. It is possible to guide the back pressure fluid that has sunk into the gap between the support plate and the rotary cylinder member to the low pressure side portion of the cylinder chamber. In this case, since the high-pressure back pressure fluid can be collected in the cylinder chamber before compression, the back pressure can be effectively used. Further, since the back pressure that tends to press the rotary cylinder in the thrust direction is reduced, it is possible to reduce the loss of the driving force of the rotary cylinder member and improve the operating efficiency.

Further, in the rotary type cylinder device according to the third aspect, the back pressure fluid is guided to the back pressure fluid escape by the orbital step portion provided on the outer edge of the cylinder support plate and guided to the low pressure side portion of the cylinder chamber. You can

Further, in the rotary type cylinder device according to the fourth aspect, the plurality of grooves radially provided on the surface of the cylinder support plate on the side of the rotary cylinder member cause the spine to sneak into the gap between the rotary cylinder member and the cylinder support plate. The pressure fluid can be guided to the back pressure fluid escape. Also,
Even when there is a large amount of back pressure fluid, it is easy to let the back pressure fluid escape.

Further, in the rotary type cylinder device according to the fifth aspect of the invention, the lubricating fluid is introduced in the process of guiding the back pressure fluid from the gap by the concave fluid reservoir formed in the center of the surface of the cylinder support plate on the side of the rotary cylinder member. Can be stored.

Further, in the rotary type cylinder device according to the sixth aspect, a plurality of pistons and cylinder chambers are formed, and the plurality of cylinder chambers are formed so as to intersect with each other including 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.

[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 an exploded perspective view of a rotary cylinder device.

FIG. 3 is a perspective view showing a structure of a cylinder support plate.

4 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. 5 is a plan view of a piston.

FIG. 6 is a side view of the piston.

FIG. 7 is a plan view of a rotary cylinder member.

FIG. 8 is a bottom view of the rotary cylinder member.

FIG. 9 is a development view of a peripheral surface of a rotating cylinder member.

FIG. 10 is a side view of a piston holding member.

11A and 11B show dimple shapes, FIG. 11A is a perspective view showing a first example, FIG. 11B is a perspective view showing a second example, and FIG.
[Fig. 6] is a perspective view showing a third example.

FIG. 12 is a conceptual diagram showing a relationship between a piston holding member and a locus during rotation of the piston.

FIG. 13 is a schematic configuration diagram of a lubricant circulation mechanism.

FIG. 14 is a view for explaining the operation of the rotary cylinder device of FIG. 1, showing a state in which one piston crosses the cavity and the other piston enters the innermost part of the cylinder chamber.

15 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.

16 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.

17 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.

18 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.

19 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.

FIG. 20 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. 21 is a plan view showing a third embodiment of the rotary cylinder device of the present invention and showing the relationship between the rotary cylinder member and the piston.

FIG. 22 is a vertical cross-sectional view of a rotary cylinder device in which the back pressure fluid relief is extended to reach the upper edge of the inner peripheral surface of the casing.

FIG. 23 is an exploded perspective view of a rotary cylinder device in which the back pressure fluid relief is extended so as to reach the upper edge of the inner peripheral surface of the casing.

FIG. 24 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. 25 is a conceptual diagram showing an example in which a cylinder chamber is formed by being offset.

FIG. 26 is a conceptual diagram showing how a corner of a hollow portion of a rotary cylinder member is chamfered.

FIG. 27 is an exploded perspective view showing a conventional rotary cylinder device.

28 is a view for explaining the operation of the rotary cylinder device of FIG. 27, (A) showing a state in which two pistons have reached the middle parts of the two cylinder chambers, FIG.
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.

[Explanation of symbols]

1 Rotary type cylinder device 2 Rotating cylinder member 22,23 Cylinder chamber 3,4 piston 5 Piston holding member 6 casing 61 Suction port (fluid inlet) 62 Discharge port (fluid outlet) 63 Back pressure fluid relief 71 Cylinder support plate 71a Back pressure fluid passage groove 71b radial groove 71c Orbital step 71d fluid reservoir O Rotational axis of rotating cylinder member X Center of rotation of piston holding member

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Katsuhiko Hayashi             2 Stock Association at 10801 Hara-mura, Suwa-gun, Nagano Prefecture             Inside Sanwa Seiki Seisakusho Suwa Minami Factory F term (reference) 3H040 AA07 BB01 CC05 CC14 DD03                       DD07 DD08 DD12 DD20 DD22                       DD23 DD27 DD28                 3H076 AA04 BB10 BB17 BB21 BB26                       CC31 CC61

Claims (6)

[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, and an inner peripheral surface of the casing that comes into contact with the rotary cylinder member so as to communicate the gap between the casing and the rotary cylinder member with the cylinder chamber. Back pressure fluid escape, and the piston is placed at a constant distance from the center of rotation of the piston holding member. The back pressure fluid that is held in a position and rotatable about the position and leaks from the cylinder chamber when the pressure is high and goes into the gap is guided to the cylinder chamber before the compression stroke by the back pressure fluid escape. Rotary type cylinder device. 2. A rotary cylinder member having a cylinder chamber formed so as to pass through the axis of rotation and rotating about the axis of rotation, a piston which makes reciprocating linear movement 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, a cylinder support plate interposed between the casing and the rotary cylinder member to rotatably support the rotary cylinder member, the cylinder support plate and the rotary cylinder member. The rotary cylinder of the casing so that the gap between the cylinder chamber and the cylinder chamber communicates with each other. A back pressure fluid relief provided on an inner peripheral surface in contact with the member; and a back pressure fluid passage groove provided on the cylinder support plate so as to communicate with the back pressure fluid relief. The back pressure fluid is held at a position a certain distance from the center of rotation of the member and is rotatable about that position, and the back pressure fluid that leaks from the cylinder chamber at high pressure and sneaks into the gap is released. And a back pressure fluid passage groove that guides the fluid into a cylinder chamber before a compression stroke. 3. The rotary cylinder device according to claim 2, wherein the back pressure fluid passage groove includes a circular step portion provided on an outer edge of the cylinder support plate. 4. The rotary type according to claim 2, wherein the back pressure fluid passage groove is provided with a plurality of grooves radially provided on a surface of the cylinder support plate on the side of the rotary cylinder member. Cylinder device. 5. The rotary cylinder device according to claim 2, wherein a concave fluid reservoir is formed in the center of the surface of the cylinder support plate on the rotary cylinder member side. 6. 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. 5. The rotary cylinder device according to any one of 1 to 5.