JPS63227901A - Rotary piston type hydraulic machine - Google Patents

Abstract

PURPOSE:To obtain a high efficiency fluid machine by fitting a plural number of rotary pistons fixed to a central rotor into a ring cylinder, with a plural number of gate valve casings being provided to be connected thereto partly so as to obtain a fluid machine unit, and combining these units together. CONSTITUTION:A plural number of gate valve cylinders 2 are attached to a part of a ring cylinder 1 at an equal angular interval, and a disk-shaped power transmitting rotor 4 is housed in the center protected by a cover 3, of the ring cylinder 1. Rotary pistons 5, 5 that are caused to move rotationally within the cylinder 1 are fixed to the outer periphery 4a of the rotor 4. A rotary gate valve 7 is provided within a gate valve casing 2 so that its rotational movement causes a cylinder chamber 6 within the cylinder 1 to open and close, and a suction opening 12, a discharge opening 13, and a transfer port 13a are drilled respectively in the neighborhood of the piston passage hole 11 of the casing 2, in the cylinder chamber 6. A fluid machine unit being composed of, as stated, is combined plurally and a desired fluid machine is obtained.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention employs a rotary piston system to
This invention relates to rotary piston fluid machines that can be applied to expansion machines, internal combustion engines, pumps, water turbines, etc.

(Prior art) In conventional reciprocating compressors, internal combustion engines, etc., the reciprocating motion of the piston is converted into rotational motion via a crank mechanism, which causes vibration, noise, and inertial energy loss associated with the reciprocating motion of the piston. , not only is it difficult to avoid the occurrence of friction loss in the crank mechanism, but the installation space for the crank mechanism is also required, which leads to larger dimensions, increased weight, and increased number of parts. The disadvantage is that the cylinder spaces on both sides of the cylinder are not utilized effectively at the same time.

For this reason, as a rotary piston type engine, for example, Japanese Utility Model Publication No. 12-16566 has a rotary gate valve, while Japanese Patent Application Laid-open No. 49-86705 has a rotating type engine.
A swing type gate valve is disclosed, and furthermore, in Japanese Patent No. 28300 and Japanese Patent Application Laid-Open No. 50-4406, a plurality of rotary fluid mechanical units of the same type are arranged in parallel, and a compression ( A compressor (compressor) and an expansion valve are separately communicated with each other.

In the WANKEL rotary piston type, the power transmission rotor does not rotate in a perfect circle, but performs eccentric rotation, so vibrations, noise, and
It is difficult to avoid the occurrence of inertial energy loss and friction loss of the perfect circular rotation conversion mechanism.

(Problems to be Solved by the Invention) However, in the conventional example of the rotary piston type described above, in the final compression process of the compression machine, the remaining compressed gas in the top clearance in the cylinder is released directly to the atmosphere. Alternatively, since it was hardly used, there was a problem that there was a lot of waste and the compression volumetric efficiency decreased.

In view of the above, the present invention is a rotary piston type, and when used as a compression machine, effectively transfers and recovers residual compressed gas to the top clearance in the cylinder in the final step of the compression cycle, thereby eliminating waste. The purpose is to provide a product with improved compression volumetric efficiency.

(Means for Solving the Problems) In order to achieve the above object, the present invention has a plurality of fluid mechanical units that are directly connected to the same power transmission shaft in a small size, and all of the fluid mechanical units are connected directly to the same power transmission shaft. A certain number of fluid machine units can be used as a compression machine or an expansion machine, or a certain number of fluid machine units can be used as a compression machine and the remaining number can be used as an expansion machine, and a combustion device can be installed thereon to use it as an internal combustion engine, and the fluid machine unit can be used as an internal combustion engine. A plurality of these fluid mechanical units to be used are sorted into groups of two units, and each set of two units in each group is provided with a specific phase difference in the compression process, so that one unit When the compression cycle is in the final step, the compressed gas remaining in the top clearance of the cylinder chamber is transferred to another unit in the middle step of the compression cycle by opening the transfer valve synchronously just before opening the gate valve. After the cylinder chamber of the unit is transferred and recovered via a connecting pipe that connects the cylinder chambers of both units with a transfer valve in between, the gate valve is opened and the rotary piston is passed through, and then the gate valve is closed and the compression cycle begins. restarts from the initial process again,
The two units repeat the above-mentioned compression process with each other, thereby greatly improving the compression volumetric efficiency.

(Function) Out of a set of two fluid machine units used as a compression machine, the residual compressed gas is transferred to the top clearance in the cylinder of one unit in the final stage of the compression cycle by opening the valve and passing it through the conduit. The compressed air is transferred to and recovered from the cylinder of another unit at an intermediate stage of the compression cycle, thereby greatly improving compression volumetric efficiency.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings.

In FIGS. 1 to 4, the fluid mechanical unit U includes a donut-shaped annular cylinder 1, and one or more gate valves (two in the figure) mounted at equal radial intervals on a part of the cylinder 1. A casing 2.2, a cover 3 covering the central part of the cylinder 1, and this cover 3
A disc-shaped power transmission rotating body 4 is housed inside the cylinder 1 so as to be rotatable in a hermetically sealed manner and performs a power transmission function. A rotary piston 5.5 that slides and rotates in a hermetically sealed manner, and a daruma that is housed in the gate valve casing 2 in a hermetically slidable manner and rotates to close and release the cylinder chamber 6 formed in the cylinder 1 for a certain period of time. It has a rotary type gate valve 7.7.

The gate valve casing 2 is formed into a cylindrical shape, and has circular side plates 9°9 disposed facing each other at intervals so as to form a gate valve storage chamber 8 therein, and these side plates 9.
, 9, and a circumferential plate 10 for closing the outer peripheral ends of the cylinders.

A part of the side plate 9 crosses the cylinder 1 and the rotating body 4
A piston passage hole 11.11 having the same diameter as the cylinder chamber 6 is bored in the inserted part so that the piston 5 can pass therethrough.
The cylinder chamber 6 and the gate valve storage chamber 8 are configured to communicate with each other when the gate valve 7 opens the passage hole 11.

A suction port 12, a discharge port 13, and a transfer port 13g are provided in the vicinity of the passage hole 11 of the cylinder chamber 6, respectively, and these suction port 12, discharge port 13, and transfer port 13a are
A known valve mechanism is connected. This transfer port 13a and the valve mechanism connected thereto are for use in a compression machine or a compression machine used in combination with an expansion machine for an internal combustion engine.

The gate valve 7 rotates within the valve storage chamber 8 around a valve shaft 14, and the valve shaft 14 projects outside through a bearing portion 15 formed near the intersection of the side plate 9 and the cylinder 1. The tip is connected to a linking/operating mechanism (not shown) for opening and closing the gate valve 7 in synchronization with the start and end of passage of the piston 5.

Further, the gate valve 7 is shown in FIGS. 5(a) to 5(d).
As shown in FIG. 2, there is a first sliding surface 16 on which the peripheral surface 4a of the rotating body 4 and the peripheral surface of the gate valve 7 slide, and a second sliding surface on which the inner surface of the side plate 9 and the gate valve 7 slide. Moving surface 17
It has

The first sliding surface 16 is provided with a pressure sealing ring (pressure sealing piece) 20 and an oil retaining ring (oil retaining piece) that perform pressure sealing and lubrication between the gate valve 7 and the peripheral surface 4a of the rotating body 4. ) 21 are provided. The shape of the first sliding surface 16 is a composite curved surface of a cylindrical body formed by the peripheral surface 4a of the rotating body 4 and a cylindrical body formed by the peripheral surface of the gate valve 7. The peripheral sliding surface on the fourth side is formed with a radius r centered on the valve shaft 14 of the gate valve 7. Further, the sliding surface around the gate valve 7 side is formed with a radius R centered on the drive shaft 23 of the rotary body 4, which will be described below, and a central portion thereof is recessed.

Thereby, the sliding surface between the peripheral surface 4a of the rotating body 4 facing the cylinder chamber 6 and the peripheral surface 16 of the gate valve 7 maintains good airtightness.

On the second sliding surface 17, an oil retaining ring (oil retaining piece) 18 is provided, in which a part of the peripheral surface 4a side of the rotating body 4 is cut out.
and a pressure sealing ring (pressure sealing piece) 19 are provided. Note that the oil retaining ring 18 and the pressure sealing ring 19 may be provided on the gate valve casing 2 side.

The rotating body 4 is provided with a drive shaft 23 at its center, and this drive shaft 23 penetrates the bearing portion 3a (see FIG. 3) of the cover 3 and protrudes to the outside. The side part of the cover 3 is strong against the cylinder 1.
A pressure sealing ring (pressure sealing piece) 24 and an oil retaining ring (oil retaining piece) 25 are provided on the peripheral side surface 4b of the inner surface near the rotary piston 5. There is a moving contact.

As shown in FIGS. 6 and 7, the rotary piston 5 has a shape in which a cylinder is curved to match the radius of the cylinder 1, that is, a donut-shaped ring so that it can slide inside the cylinder chamber 6. The pressure sealing ring 26 (pressure sealing piece) and the oil retaining ring (oil retaining piece) 27, which have a cut-off shape and are attached to the periphery thereof, are used when the rotary piston 5 passes through the passage hole 11 of the gate valve. If the thickness W of the rings 26 and 27 is smaller than the gap width g of the valve storage chamber 8 (Fig. 4), the direction of rotation of the rotating body 4 is If the thickness W is large, the cylinder 1 is installed parallel to the radial direction of the cylinder 1 as shown in FIG.

By configuring the rings 26, 27 in this way, when the rotary piston 5 passes through the gap in the valve housing chamber 8 of the gate valve casing 2, the rings 26, 27 will not fly out into the valve housing chamber 8. There is no.

Further, after the gate valve 7 closes the piston passage hole 11 formed in the side plate 9 of the gate valve casing 2,
The lower part 18a of the ring piece 18.19 provided on the gate valve 7 faces the second sliding surface 17 of the gate valve 7 and rotates clockwise when it is released across its piston passage hole 11.

In order to prevent the piston passage hole 19a from getting caught on the periphery of the piston passage hole 11 of the gate valve casing 2, as shown in FIG. A valve 28 and a ring 29.30 may also be formed.

FIG. 9 shows an example in which two of the fluid mechanical units U are used in combination, and a reciprocating type gate valve is used instead of the rotary type gate valve.

That is, 2 having pistons 32 and 33 on the power transmission shaft 31
Two rotating bodies 34.35 are installed at intervals, and these rotating bodies 34.35 are housed in a cover 36 having bearing parts 36a, 36a, and a reciprocating type is installed so as to bridge both rotating bodies 34.35. A gate valve casing 37 is provided.

A rectangular gate valve storage chamber 38 is provided in this gate valve casing 37, and a reciprocating type gate valve 42 is stored inside this storage chamber 38 and can be slid left and right in a hermetically sealed manner.
An oil retaining ring 40 and a pressure sealing ring 41 are provided on any appropriate side of the two sides, and a connecting portion 43 that interconnects the two gate valves 42 and 42 and a connecting portion 43 that operates the gate valves 42 left and right. It has a protrusion 44 that is connected to the gate valve 42 and protrudes to the outside as a power transmission rod for this purpose.

In addition, in order to reduce resistance due to compression and expansion of the gas in the valve storage chamber 38 when the gate valve 42 rapidly operates from side to side, the left and right sides of the valve storage chamber 38 are connected by a gas pressure equalizing conduit 45. There is.

The shape of the sliding surface 39 between the peripheral surface of the gate valve 42 and the peripheral surface of the rotating body 34.35 is a cylindrical curved surface with a radius R centered on the power transmission shaft 31 of the rotating body 34.35. The sliding surface 39 of the gate valve 42 has a concave central portion. This sliding surface 39 has parts shown in FIG. 9(b) and (
As shown in c), a pressure sealing rod-like piece 40a and an oil-holding rod-like piece 41a are provided on the gate valve 42 side.

Further, the cross section of the cylinder is not limited to a circular shape, and may be an elliptical cylinder 46 (FIG. 10), a rectangular cylinder 47 (FIG. 11), or other shapes as necessary.

When the piston ring is provided obliquely as shown in FIG. 6, if the cross-sectional shapes of the cylinder and rotary piston are elliptical, the piston ring can be made into a perfect circle.

In FIG. 9, the reciprocating type gate valve 42 is integrally formed by bridging both rotary bodies 34.35, but the reciprocating type gate valve 42 may be provided separately for each rotary body 34.35. Furthermore, the Daruma-shaped rotary gate valve may be provided individually. In this case, mounting gate valves on multiple annular cylinders has the advantage that the position angle can be set arbitrarily, so it is sufficient to select the appropriate gate valve depending on the purpose.

Next, application examples of the present invention using the above fluid mechanical unit will be described.

The fluid machine of the present invention consists of a combination of one or more fluid machine units directly connected to the same power transmission shaft in a skewer shape, and is applicable to compression machines, expansion machines, internal combustion engines, pumps, water turbines, etc. It's Chino.

FIG. 12 shows an operation cycle in which this fluid machine is adapted to a compression machine, in which the first fluid machine unit U1 and the second
The fluid mechanical unit U2 is directly connected and driven to the same power transmission shaft in a skewer type, and the left and right units U, U2 have two pistons 50 and 51 provided at equal intervals, respectively, with reference to the gate valve casing 56 and 57. A phase angle difference on the compression cycle of 90° from each other is provided. Therefore, the opening and closing timings of the two gate valves 52 and 53 provided in each of the units U 1 and U 2 when the piston passes are not the same, but operate independently and mutually.

Fluid mechanical unit U 1. First cylinder 54 of U2
and a gate valve casing 56 of the second cylinder 55,
57 are each provided with an inlet port 58a.

58b and discharge ports 59a and 59b are provided. Discharge ports 59a of both cylinders 54,55.

59b and compressed air storage tank 60 are connected to conduits 65, 66°, 67.
68, 69 and 70 and controlled by four discharge valves 61, 62, 63 and 64.

At an intermediate position of the conduits 69,70 there is a transfer valve 71.
72 are provided. .

In FIG. 12(T), the piston 50 of the first cylinder 54 is at a position immediately after passing through the gate valve casing 56, that is, at the beginning stage of the compression cycle, and the piston 51 of the second cylinder 55 is at the intermediate stage of the compression cycle. The rotating bodies 73 and 74 of both fluid mechanical units U and U2 are rotating in the direction of the half-hour hand.

Note that at this time, the gate valves 52.53 of both cylinders 54.55 are closed, and in all figures other than FIG. 12 (V2), the gate valves 52.53 are closed.

Gas is sucked into the cylinder 54.55 from the intake ports 58a and 58b of both cylinders 54.55 in FIG. Compression is performed in the compression chambers c, c..., new gas is sucked into the suction chambers s, s... on the opposite side, and discharge valves 61, 62, 63, . 64 and transfer valve 71
．． All 72 are closed.

From this state, the piston 50.51 rotates counterclockwise as shown in (II) and (2) of the same figure, and the gas in the compression chamber C of the second cylinder 55 is compressed to a predetermined pressure or higher. Then, the discharge valves 63 and 64 on the second cylinder 55 side of the compressed gas gas storage tank 60 open, and the compressed gas flows into the gas storage tank 60. At this time, the first cylinder 54
is in the middle stage of the compression cycle, and the discharge valve 63°6
All other valves except 4 are closed.

Furthermore, as shown in the same figure (III), the second cylinder 55
When the piston 51 approaches the position immediately before the opening operation of the gate valve 53, the transfer valve 71.72 opens and the discharge valve 63.6 of the compressed gas storage tank 60 opens.
4 is closed, the compressed gas remaining in the top clearance in the compression chamber C of the second cylinder 55 is transferred and collected through the conduit 69.70 into the compression chamber C of the first cylinder 54 in the intermediate stage of the compression cycle. .

Therefore, the gas pressure in the compression chamber C of the second cylinder 55 decreases, thereby reducing the pressure on the side surface of the gate valve 53, which reduces the sliding resistance of the gate valve 53 and facilitates its high-speed operation. In addition, the second cylinder residual compressed gas that has flowed into the compression chamber C of the first cylinder 54 increases the pressure of this compression chamber C and improves the compression volume efficiency of the first cylinder.

When the pistons 50 and 51 rotate further from this state, the gate valve 53 of the second cylinder 55 is opened, the piston 51 passes through the opening of the gate valve casing 57, and immediately after this passage, the gate valve 53 is closed. hand,
The compression cycle is started again. At this time, the first cylinder 54 is in the middle stage of the compression cycle and the piston 54 is in the middle stage of the compression cycle.
When the piston 50 of the first cylinder 54 approaches the gate valve 52 and the pressure in the compression chamber C exceeds a certain level, as shown in FIG. Valves 61 , 62 are opened and compressed gas flows into this compressed gas storage tank 60 .

When the piston 50 of the first cylinder 54 advances from this state to the state shown in the figure (V) (corresponding to the state of the second cylinder 55 in the figure (III)), the transfer valve 71. 72 is opened, the discharge valves 61 and 62 of the compressed gas storage tank 60 are closed, and the first cylinder 54 is opened.
The remaining compressed gas flows into the compression chamber C of the second cylinder 55, and the above-mentioned effect of improving the compression volume efficiency of the second cylinder is produced.

When the gate valve 52 of the first cylinder 54 is opened, the piston 50 passes through the gate valve casing 56 and returns to the state shown in (1) in the same figure, as shown in FIG. Repeat.

The compressed gas thus stored in the compressed storage tank 60 is taken out to the outside to do work.

Fig. 13 shows the operating cycle when this fluid machine is applied to an internal combustion engine, in which the first unit U3 functions as an expansion machine and the second unit U4 functions as a compression machine.
are directly connected to the same power transmission shaft in a skewer shape, and the two units U 3 and U 4 each have two pistons 82 and 83 and two gate valves 105 and 108 at equal intervals.
The phases of the expansion process on the expansion cycle of the first cylinder 80 and the compression process on the compression cycle of the second cylinder 81 have a specific phase angle difference (90° in the figure) with respect to the gate valve. This is provided.

A compressed air storage tank 84 is provided between the two cylinders 80.81, and a filling valve 85.
86 and discharge valves 87 and 88 are provided, and a filling port 91a and a discharge port 92 are provided near the gate valve casings 89 and 90 of the first cylinder 80 and the second cylinder 81, respectively.
b is formed. Filling port 91a of first cylinder 80
and the discharge port 92b of the second cylinder 81.
A conduit 97.98 protruding from the compressed air storage tank 84 and having the discharge valve 87.88 at the open end of the air storage tank is connected to the conduit 93.94, and a transfer valve 99, 100 is installed.

In addition, although it is omitted in the drawing except for the same drawing (V construction),
As shown in this figure, scavenging conduits 101 and 102 are provided,
One end of these scavenging conduits 101, 102 is connected to the first cylinder 80.
exhaust port 91b.

91b, and a scavenging valve 103 is located in between.
．． 104 are provided, the other ends of which are connected to the conduits 93 and 94, respectively.

In this embodiment, the first unit U3 acts as an expansion machine and the second unit U4 acts as a compressor for storing compressed air in the compressed air storage tank 84. Both units U3. The rotating bodies 106 and 107 of U4 rotate counterclockwise, and the figure (I) shows the position immediately after the piston 82 of the first cylinder 80 passes this gate valve 105
The gate valve 105 is in a state where the first cylinder 80 has been completely closed, that is, the first cylinder 80 is on the verge of starting an explosion-expansion cycle, and the second cylinder 82 is in an intermediate stage of a compression cycle.

As the piston 82 advances further, the filling valves 85 and 86 of the compressed air storage tank 84 reach the state shown in the figure (■□).
is opened and compressed air enters the expansion chambers e, e of the first cylinder 80 via conduits 95, 96.

In the case of a diesel engine, fuel is injected from a nozzle (not shown) at this time and an explosion occurs, and in the case of a gasoline engine, the compressed air from the compressed air storage tank 84 is transferred to a vaporizer provided near the filling port 91a. vessel (not shown)
The fuel and air mixture gas is injected into the expansion chamber e via the
The ignition device ignites the fire, causing an explosion, and eventually the same figure (
■Proceed to the state shown in 2).

On the other hand, the exhaust chamber X formed at the front surface of the first cylinder 80 in the direction of movement of the piston 82 has started an exhaust cycle. Further, the piston 83 of the second cylinder 81 approaches the closed gate valve 108 while compressing the air in the compression chambers C and C, and when the air pressure therein reaches a certain level or higher, the discharge valves 87 and 88 are opened. However, the compressed air is stored in a compressed air storage tank 84. At this time, the filling valve is 85°8
6 is closed.

As shown in Figure (III), when the piston 83 of the second cylinder 81 further approaches this gate valve 108,
While the discharge valves 87 and 88 are closed, the transfer valves 99 and 100 are opened, and the residual compressed air in the compression chamber C flows into the expansion chamber e in the first cylinder 80, and the piston 8
2 is accelerated. At the same time, the opening/closing operation of the gate valve 108 of the second cylinder 81 is facilitated by the operation described in the embodiment of the compressor.

While the gate valve 108 of the second cylinder 81 is open, this piston 83 is inserted into the gate valve casing 90.
Pass through 1. After the initial stage of the compression cycle, the same figure (I
As shown in V), upon entering the intermediate stage of the compression cycle,
The piston 82 of the first cylinder 80 is connected to the gate valve 10
5, and exhaust is performed, but at this time, the same figure (V
As shown in 1), the scavenging valves 103 and 104 are momentarily opened, and the slightly higher pressure air in the first cylinder 80 flows into the exhaust chambers x and x.

Promote exhaustion of residual combustion gases of X.

Immediately after the exhaust is finished, the gate valve 105 of the first cylinder 80 is opened, and the piston 82 passes through the gate valve casing 89, as shown in FIG.
The state shown in FIG. 3(I) is returned, and the operation cycle is thus repeated.

The setting positions of the above-mentioned discharge valve, transfer valve, filling valve, scavenging valve, etc. are shown arbitrarily for convenience of explanation, but in actual application, the optimum position should be selected in terms of performance, manufacturing, etc. do.

In addition, although the number of pistons and gate valves in one cylinder is two in this embodiment, it is not limited to this, and the number of pistons and gate valves in one cylinder is not limited to two. It goes without saying that the number of units can be appropriately selected depending on usage, performance, capacity, etc.

Incidentally, in a two-piece fluid machine unit used as a compression machine, each cylinder has n rotary pistons and n gate valves, which is calculated as 22/2. That is, the phase cycle difference is set to 1/2 cycle.

(Effects of the Invention) Since the present invention has the above configuration, it can be applied to compression machines, expansion machines, internal combustion engines, pumps, water turbines, etc., so it has a wide range of applications.Moreover, as a fluid machine, each functional part is symmetrical. Since it is simply and rationally arranged and configured, there is little waste, and the device can be made smaller and lighter, and the number of parts can be reduced, and as a result, costs can be reduced.

Moreover, as mentioned above, when a set of two fluid mechanical units is used as a compression machine, when one unit is in the final stage of the compression cycle, the compressed gas remaining in the top clearance of the cylinder is transferred to the other unit. Since it can be effectively transferred and recovered into the cylinder at an intermediate stage of the compression cycle of the unit, the compression volumetric efficiency can be greatly improved.

[Brief explanation of the drawing]

Fig. 1 is a perspective view of the fluid mechanical unit, Fig. 2 is a perspective view of the internal structure of Fig. 1, Fig. 3 is a sectional view taken along the line m-■ in Fig. 1, and Fig. 4 is a - Sectional view along line IV, No. 5
Figures (a) and (b) are perspective views of the rotary gate valve, Figures (C) and (d) are explanatory diagrams for explaining the shape of the rotary gate valve, and Figures 6 and 7 are respectively A front view of a rotary piston with a hole, Figure 8 is a front view showing another example of a rotary gate valve, and Figure 9 (a) is a longitudinal cross-section of a reciprocating gate valve in which two units are arranged in parallel. FIGS. 10 and 11 are cross-sectional views showing the cross-sectional shape of another cylinder, which is a hole, respectively. The figure is an operating cycle process diagram when this fluid mechanical unit is applied to a compression machine, and FIG. 13 is an operating cycle process diagram when this fluid mechanical unit is applied to an internal combustion engine that is a combination of a compression machine and an expansion machine. DESCRIPTION OF SYMBOLS 1... Cylinder, 2... Rotary gate valve casing, 3... Cover, 4... Rotating body, 5...
Rotary piston, 7... rotary gate valve,
23... Power transmission shaft, 37... Reciprocating type gate valve casing, 42... Reciprocating type gate valve,
54.55.81... Cylinder of compressor machine unit,
80... Cylinder of expansion machine unit, 60... Compressed gas storage tank, 61, 62, 63, 64, 87° 88.
...Discharge valve, 71.72...Transfer valve, 84.
...Compressed air storage tank, 85.86...Filling valve, 9
9.100...Transfer valve, 103,104...Scavenging valve. Applicant's representative Sato-O (d) Section 9, Haya 12 Figure Vl Bara 12 Figure Tsuri I3 Inyu 13th Procedure Amendment Form) % Formula % 2. Name of Invention Rotary Piston Fluid Machine 3, Amendment Patent applicant Kagami Yamaroku Bu 4, agent (zip code 100) February 3, 1983 (shipment date February 23, 1988) 6. Power of attorney and drawings subject to amendment 7. Contents of amendment (1) The power of attorney will be amended as shown in the attached sheet.

Claims (1)

[Claims] 1. A rotary piston type fluid machine consisting of a combination of a plurality of rotary piston type fluid machine units,
The fluid mechanical unit includes a donut-shaped annular cylinder having a ring-shaped slit in a circumferential wall on the center side of the cylinder on a plane including the annular center line of the cylinder, and a donut-shaped annular cylinder that is rotatably arranged in the center of the cylinder and has an outer circumferential side wall formed with the slit. a rotating body that slides in a closed manner around the opening on the center side of the cylinder; a power transmission shaft that is connected to the center of the rotating body and rotates together with the rotating body; one or more rotary pistons that slide in a hermetically sealed manner; and a rotary piston that is provided in a slit portion at a specific location of the cylinder and that is capable of protruding and retracting the cylinder in a direction perpendicular to the annular center line of the cylinder; It consists of a gate valve that closes the chamber and opens it when the chamber is pulled back.These gate valves, which are provided in the same number as the rotary pistons, operate in synchronization with the rotary piston, and open the cylinder chamber when the rotary piston starts passing. death,
The rotary piston is configured to close this area at the end of its passage, and a plurality of these fluid mechanical units are directly connected to the same power transmission shaft in a skewer shape, and all of the fluid mechanical units are compressed. A certain number of these fluid machine units are used as compression machines and the remaining number are used as expansion machines, and a combustion device is provided to this and used as an internal combustion engine, and this fluid machine unit used as the compression machine is Multiple fluid machinery units are sorted into groups of two units, and two of each group are
A set of individual units has a specific phase difference between them in the compression process, and when one unit is in the final process of the compression cycle, the compressed gas remaining in the top clearance of the cylinder chamber is removed immediately before the gate valve is opened. Then, the transfer valves are opened synchronously, and the transfer and recovery is carried out into the cylinder chamber of the other unit in the middle stage of the compression cycle via the connecting pipe that connects the cylinder chambers of both units with the transfer valve interposed. After that, the gate valve is opened to allow the rotary piston to pass through, and then the gate valve is closed, and the compression cycle restarts from the initial step, and the two units repeat the above compression process with each other, thereby increasing the compression volumetric efficiency. A rotary piston type fluid machine characterized by improved width. 2. Claim 1, characterized in that a pressure sealing piece and an oil retaining piece are provided on the outer circumferential surface of the rotary piston that is displaced relative to the inner surface of the cylinder chamber.
The rotary piston type fluid machine described in . 3. The gate valve is housed in a gate valve casing in a reciprocating and sealed sliding manner, and the gate valve has a sealed sliding surface with the gate valve casing and a sealed sliding surface with the rotating body of the gate valve, respectively. A pressure sealing piece and an oil retaining piece are provided, and the gate valve casing is attached to the cylinder casing perpendicularly across the annular centerline of the cylinder and has a substantially rectangular cut surface, and the adhesive side wall facing the cylinder has a substantially rectangular cut surface. The gate valve is partially embedded in a specific slit of the cylinder casing in a sealing manner, and the adhesive side wall is provided with a passage hole for a rotary piston that communicates with an opening inside the cut surface of the cylinder casing. When the rotary piston reciprocates in synchronization with the movement of the rotary piston, the piston passage hole of the gate valve casing opens and closes synchronously when the piston begins to pass and closes when the piston ends. A rotary piston type fluid machine according to claim 1. 4. The plurality of rotary pistons are arranged at equal intervals on the outer peripheral surface of the rotary body, and the same number of gate valve casings including the gate valves are arranged at equal intervals within the cylinder casing corresponding to the number of the rotary pistons. The rotary piston type fluid machine according to claim 1, characterized in that the rotary piston type fluid machine is arranged as follows. 5. A pressure sealing ring and an oil retaining ring are provided on the sealing sliding surface of the rotating body with the cylinder casing, and the power transmission shaft is connected to the center of the rotating body and rotates integrally with the rotating body. The rotary piston according to claim 1, wherein the rotary piston is rotatably supported by bearing portions of a pair of covers, and the covers are integrally connected to the cylinder casing and disposed facing each other. formula fluid machine. 6. The shape of the inner surface of the cylinder casing and the cut surface perpendicular to the cylinder center gland of the rotary piston is circular, elliptical, rectangular, or other shape, and the part that constitutes the entire fluid mechanical unit including the cylinder. The shape of the claim is characterized in that the whole unit can be divided into two or more symmetrical shapes perpendicular to the direction of the power transmission axis, and each part is formed symmetrically. A rotary piston type fluid machine according to scope 1. 7. The gate valve is rotatably and slidably housed in a gate valve casing, and the gate valve casing is attached to the cylinder casing so as to perpendicularly cross the annular center line of the cylinder, and has a substantially smooth cylindrical shape. , the opposing side walls are partially sealingly embedded in a specific slit of the cylinder casing, and each side wall is provided with a piston passage hole communicating with the inner peripheral surface of the cylinder, The gate valve is rotatably attached to the side wall, and the piston passage hole opens and closes synchronously when the rotary piston starts to pass and closes when the piston ends to pass. The rotary piston fluid machine according to item 1.