WO2016095757A1 - 旋转活塞式工作机 - Google Patents

旋转活塞式工作机 Download PDF

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Publication number
WO2016095757A1
WO2016095757A1 PCT/CN2015/097129 CN2015097129W WO2016095757A1 WO 2016095757 A1 WO2016095757 A1 WO 2016095757A1 CN 2015097129 W CN2015097129 W CN 2015097129W WO 2016095757 A1 WO2016095757 A1 WO 2016095757A1
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WIPO (PCT)
Prior art keywords
piston
cylinder
sealing member
annular
seal
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PCT/CN2015/097129
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English (en)
French (fr)
Inventor
郑福建
郑创想
郑语晗
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郑福建
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Publication of WO2016095757A1 publication Critical patent/WO2016095757A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons

Definitions

  • the invention belongs to the technical field of internal combustion engines or air compression, and in particular relates to a rotary piston working machine.
  • a reciprocating piston internal combustion engine is commonly used.
  • the piston reciprocates linearly in the cylinder, and the linear motion of the piston is converted into a rotary motion as a power output through a crank-link mechanism, which has a complicated structure, a large space, and many moving parts.
  • the friction between the parts with non-circular motion is large, which not only has high manufacturing cost and is easy to be damaged, but also causes the engine to be unbalanced due to the periodic variation of the reciprocating inertial force, causing vibration to cause noise, energy consumption, loose joints, and severe wear and tear.
  • Problems such as service life, affecting the smoothness, comfort and reliability of the internal combustion engine, can only increase the balance of balance pieces and other balance parts, but further complicate the structure of the internal combustion engine.
  • the triangular-rotor internal combustion engine currently in use is not purely circular motion and the compression ratio of the triangular-rotor internal combustion engine is low, and the triangular-rotor internal combustion engine has a poor sealing effect and difficulty in manufacturing and maintenance due to irregularities of the cylinder block and the piston. high.
  • the object of the present invention is to provide a rotary piston type working machine, which has a simpler structure, and changes the reciprocating motion of the conventional piston to work or compress the gas for the rotary motion, and the rotation speed is faster and the efficiency is higher. , the work is more stable and the service life is longer.
  • the present invention provides a rotary piston type working machine comprising an annular or disk-shaped cylinder block, wherein the cylinder block has an annular groove formed along a circumferential direction of the cylinder block, the cylinder a drive shaft is disposed on the body axis, and a first seal is connected to the drive shaft, and the first seal seals the annular groove and encloses a closed annular cylinder with the cylinder block in the annular cylinder.
  • the first seal member is provided with at least one piston, and the piston is matched with the annular cylinder; the cylinder block is provided with at least one stopper mounting opening in the circumferential direction, and a second seal supported by the rotating shaft outside the cylinder block.
  • a second sealing member is provided with at least one piston through hole, the piston rotates around the transmission shaft and moves circumferentially along the annular cylinder, and the second sealing member rotates around the rotating shaft, and the piston rotates to In the second sealing member, the second sealing member is rotated to a position corresponding to the piston through hole and the piston, so that the piston just passes through the piston through hole, and the second sealing member installs the stopper during the movement
  • the chamber is sealed on both sides of the port and the mounting port of the block, and the cylinder block is provided with an air inlet and an air outlet.
  • the body when the air inlet port and the air outlet port are respectively provided on the cylinder walls on both sides of the one-piece mounting port, the body can be used as the internal combustion engine body, and the piston is fixedly connected to the first sealing member, or can be integrally formed.
  • the first sealing member drives the transmission shaft to rotate, so that the transmission shaft directly outputs the torque, thereby reducing the energy loss caused by friction or excessive transmission components during the transmission process. Since the original reciprocating motion is changed by the rotary motion, the piston can For a plurality of symmetrical settings, the internal combustion engine is operated very smoothly, and a higher rotational speed can be achieved, and the positions of the air outlet and the air inlet can be appropriately changed according to requirements to adjust the output power.
  • the structure does not have the eccentric pressure of the piston of the reciprocating piston type internal combustion engine to the cylinder wall. Therefore, the present invention has only no contact between the cylinder block and the seal member, so there is almost no friction, which can reduce the loss of energy due to friction and can be extended.
  • the service life of the components Moreover, the dynamic balance is good, and there is no problem that the conventional internal combustion engine is unbalanced due to the cyclical change of the reciprocating inertial force, causing noise, noise, energy consumption, loose joints, severe wear and shortened service life, and the internal combustion engine has small vibration and noise. Sexuality and reliability.
  • the air outlet and the air inlet When the air outlet and the air inlet are respectively arranged on the cylinder walls on both sides of each of the block mounting ports, it can be used as an air compressor, and the power is connected to the driving piston through the transmission shaft to compress the gas, and the air can be set at this time.
  • the piston and the plurality of stopper mounting ports the gas is compressed and discharged from the air outlet to the external gas storage tank. Since the cylinder body cavity is large, the piston can rotate more than one turn to compress more gas, so that the compression efficiency is improved.
  • two pistons and two second seals divide the annular piston chamber into four chambers of the suction chamber, the compression chamber, the expansion chamber and the exhaust chamber (when a double piston is used), the piston is Rotating in the annular piston chamber, the internal combustion engine rotates once to complete the working stroke of the suction, compression, expansion work and exhaust gas twice, and is continuously performed continuously, which is equivalent to the reciprocating internal combustion engine power of the same displacement.
  • the first sealing member drives the transmission shaft to rotate, so that the transmission shaft directly outputs torque, thereby reducing the energy loss caused by friction or excessive transmission components during the transmission process; the piston is symmetrical due to the change of the original reciprocating motion.
  • the invention also provides a rotary piston working machine, comprising two cylinder blocks coaxially arranged in parallel, wherein two annular grooves are respectively formed on the two cylinder bodies, and the annular groove openings of the two cylinder bodies face each other, and the two cylinders
  • a first sealing member is interposed between the bodies, and the two annular grooves are fitted to both sides of the first sealing member to respectively form two closed annular cylinders
  • the transmission shaft is mounted on the cylinder block axis through the bearing and is connected to the first sealing member a fixed connection; at least one piston is disposed on the first seal in each annular cylinder, the piston is adapted to the annular cylinder;
  • the cylinder block is provided with at least one stopper mounting port laterally connected to the annular cylinder, and the stopper mounting ports on the same side of the two cylinder blocks are adjacent to each other to form a pair of stopper mounting ports, and the second is supported by the rotating shaft outside the cylinder block a sealing member extends into the stopper mounting opening, the second sealing member and the piston divide each of the annular cylinders into at least two chambers, and the second sealing member is provided with at least one piston through hole
  • the piston rotates around the drive shaft and moves circumferentially along the annular cylinder, the second seal rotates about the rotating shaft, and when the piston rotates to the second seal, the second seal rotates to the piston through hole and
  • the corresponding position of the piston causes the piston to pass through the piston through hole, and the second sealing member seals the block mounting opening and the chamber on both sides of the stopper mounting opening during the movement; each stopper mounting opening
  • An air inlet and an air outlet are respectively disposed on the annular cylinders on both sides, and
  • the technical solution is two parallel annular cylinders, the suction and compression are completed by the first annular cylinder, and the expansion and work are completed by the second annular cylinder, and the two cylinders are arranged side by side and divided, which is compared with the first technology described above.
  • the better effect is: 1.
  • the piston and the sealing disc and the supporting structure only need half of the first technical solution, which greatly simplifies the structure, reduces the cost and increases the performance.
  • FIG. 1 is a schematic structural view of Embodiment 1 of the present invention.
  • Figure 2 is a left side view of Figure 1.
  • FIG. 3 is a structural schematic view of the cylinder block of FIG. 1 mated with the first and second seals.
  • FIG. 4 is a cross-sectional view of the cylinder block of FIG. 3 mated with the first seal.
  • FIG. 5 is a schematic view showing the cooperation structure of the second sealing member, the piston and the first sealing member.
  • Fig. 6 is a schematic view showing the structure of the piston in the first embodiment.
  • Fig. 7 is a structural schematic view of the air inlet end check valve of Fig. 6.
  • Fig. 8 is a structural schematic view of the air outlet end check valve of the air guiding hole of Fig. 6.
  • FIG. 9 is a structural schematic view of the second sealing member of FIG. 1 mated with the cylinder block and the first sealing member.
  • Figure 10 is a schematic view showing the cooperation relationship of the first seal member, the piston and the second seal member.
  • Figure 11 is a schematic view showing the structure of the second sealing member of Embodiment 1 (only one piston through hole is shown).
  • Figure 12 is a schematic structural view of Embodiment 2 of the present invention.
  • Figure 13 is a right side view of Figure 12 .
  • Figure 14 is a schematic view showing the structure of an annular cylinder in Embodiment 2 of the present invention.
  • Figure 15 is a schematic view showing the cooperation relationship between the annular cylinder and the piston in the second embodiment of the present invention.
  • Figure 16 is a diagram showing the mating relationship after the second seal member is added in Figure 15.
  • Figure 17 is a cross-sectional view in the left-view direction of Figure 16 (cylinder block not shown).
  • Figure 18 is a schematic structural view of Embodiment 3 of the present invention.
  • Figure 19 is a right side view of Figure 18.
  • Figure 20 is a cross-sectional structural view of the annular cylinder and the plenum of Figure 18 (when the air passage is conducting the expansion chamber).
  • Figure 21 is a cross-sectional view showing the structure of the F-F of Figure 18.
  • Figure 22 is a cross-sectional view showing the structure of the G-G of Figure 18;
  • Figure 23 is a cross-sectional view showing the mating relationship between the annular cylinder and the piston of Embodiment 3 of the present invention.
  • Figure 24 is a schematic view showing the structure of the first cylinder block of Figure 23;
  • Figure 25 is a cross-sectional view showing the structure of the H-H of Figure 20;
  • Figure 26 is a schematic view showing the structure of a seal ring in the third embodiment.
  • Figure 27 is a schematic view showing the structure of the first sealing member in the third embodiment.
  • Figure 28 is a cross-sectional structural view showing the position of the sub air jet port of Figure 27;
  • Figure 29 is a schematic view showing the structure of Embodiment 4 of the present invention.
  • Figure 30 is a schematic view showing the structure of the valve plate of the jet valve of Figure 29.
  • Figure 31 is a schematic cross-sectional view showing a partial cross-sectional view of a fifth embodiment of the present invention.
  • Figure 32 is a bottom view of Figure 31 (with a gas storage combustion chamber).
  • Figure 33 is a right side view of Figure 32.
  • Figure 34 is a cross-sectional structural view of the first annular cylinder of Figure 31.
  • Figure 35 is a schematic view showing the gas distribution of the first annular cylinder of Embodiment 5 (the right-view direction of Figure 31).
  • Figure 36 is a schematic view showing the gas distribution of the second annular cylinder of Embodiment 5 (the left-view direction of Figure 31).
  • Figure 37 is a perspective view of the first seal of Figure 31.
  • Figure 38 is a cross-sectional view showing the first sealing member of Figure 31;
  • Figure 39 is a schematic structural view of an embodiment of the sixth embodiment of the present invention.
  • FIG. 40 is a schematic structural diagram of another embodiment of Embodiment 6 of the present invention.
  • Figure 41 is a cross-sectional structural view (right-view direction) of the piston of Figure 40 as it passes through the second seal.
  • a rotary piston type working machine is used for an internal combustion engine, and includes an annular cylinder block 1.
  • the cylinder block 1 has a circumference along the cylinder block 1.
  • a drive ring 21 is disposed on the axis of the cylinder block 1.
  • the drive shaft 21 is disposed at the center of the inner ring of the cylinder block 1.
  • the first seal 22 is connected to the drive shaft 21, and the first seal is connected. 22 encloses the annular groove and encloses the annular cylinder 11 with the cylinder block 1.
  • the first sealing member 22 has a disc shape, and the outer circumference of the outer circumference of the disc is low.
  • the intermediate portion of the outer circumference of the first sealing member 22 extends into the annular groove to connect with the piston 23, and seals the annular groove, and the cylinder block 1
  • the annular cylinder 11 is enclosed together.
  • the first sealing member 22 in the annular cylinder 11 is provided with two pistons 23, and the piston 23 is matched with the annular cylinder 11, and the lower portion of the outer circumference of the first sealing member 22 is fitted to the outer wall of the inner ring of the cylinder block 1,
  • a sealing member 22 seals the annular groove at all times, and the two pistons 23 are symmetrically disposed with respect to the transmission shaft 21.
  • the side wall of the cylinder block 1 is provided with an air inlet 12 and an air outlet 14.
  • the second seal 16 is disc-shaped, the outer circumference of the two second seals 16 projecting into the stop.
  • the block is installed inside the port.
  • the outer circumference of the second sealing member 16 is concave and adapted to the portion in contact with the outer circumference of the first sealing member 22, and the outer circumference of the second sealing member 16 is in contact with the first sealing member 22,
  • the two seals 22 are symmetrically opened with two piston passage holes, the first seal member 16 is concave in a portion of the annular cylinder, and the two second seal members 22 are driven by the transmission mechanism to rotate in opposite directions.
  • Two stopper mounting openings 15 are circumferentially opened on the cylinder block 1.
  • Each of the stopper mounting openings 15 is internally provided with a second sealing member 16 which is supported by a rotating shaft outside the cylinder block.
  • the outer peripheral portion of the second seal member 16 extends into the stopper mounting opening, and the second seal member 16 and the piston 23 divide the annular cylinder 11 into four chambers.
  • the rotating shaft 17 is mounted on the outer bracket 6, the two rotating shafts 17 and the two second sealing members 16 are disposed outside the cylinder block 1, and the second sealing member 16 is in the shape of a disk. As shown in FIG. 3 and FIG.
  • the intermediate portions of the outer circumferential bus bars of the second sealing member 16 and the first sealing member 22 are both concave and mutually adapted, and the structure can make the outer circumference of the second sealing member 16 and the first portion
  • the outer circumference of a sealing member 22 is kept in close contact during the rotation to achieve sealing;
  • the piston through holes 18 are two, 180 degrees symmetrically open on the second sealing member 16;
  • the plug 23 rotates around the transmission shaft 21 with the first sealing member 22, and moves circumferentially along the annular cylinder 11, and the second sealing member 16 rotates around the rotating shaft 17, and the rotating shaft 17 is vertically staggered with the transmission shaft 21, and the piston 23 is rotated to the first
  • the seal member 16 is closed, the second seal member 16 is rotated to a position corresponding to the piston through hole 18 and the piston 23, so that the piston 23 just passes through the piston passage hole 18, and the second seal member 16 will block the block mounting opening 15 during the movement. Sealed, the second seal 16 seals the block mounting opening 15 and the chambers on both sides
  • the air cylinders 12 and the air outlets 15 are respectively disposed on the cylinder walls on one side of one of the stopper mounting ports 15, and the air reservoirs are respectively disposed on the cylinder walls on the two sides of the other stopper mounting ports 15.
  • the air vent, the air vent and the air vent are connected by an air storage pipe (not shown), and the air vent and the air vent are respectively provided with a sealing valve for opening and closing the air vent and the air vent, between the air vent and the air vent
  • a gas storage combustion chamber is provided, and a spark plug or a fuel injector is provided in the gas storage combustion chamber.
  • the structure belongs to the prior art (see Chinese Patent Application Publication No. CN101684745A), which is not described herein again.
  • the piston 23 may be provided with an air guiding hole 25 extending in the longitudinal direction of the piston 23 and penetrating the front and rear portions of the piston 23, and the front and rear ends of the air guiding hole 25 are A one-way valve is provided, the two check valves are opened in the same direction, and the air guiding holes 25 between the two one-way valves form a gas storage combustion chamber, and the one-way valve can be opened at different pressure thresholds,
  • FIG. 7 and 8 is a check valve 26a, 26b which respectively shows the inlet and outlet ends of the air guiding hole 25, and adopts a structure in which a spring is connected to the trapezoidal valve.
  • the shape of the piston through hole 18 of the second sealing member 16 corresponds to the shape of the piston 23, and the front and rear sides of the piston 23 are inclined and spiral.
  • the curved surface, the left and right sides of the piston 23 are fitted to the left and right side walls of the annular cylinder 11, and the piston 23 has a fan shape on the projection of the plane of the axis of the drive shaft 21, and the piston through hole 18 is a fan hole.
  • the inner wall of the piston passage 18 remains in engagement with the outer contour surface of the piston 23.
  • the piston structure is such that the front and rear sides of the piston 23 are spiral curved surfaces having a certain degree of twist extending obliquely along the longitudinal direction of the piston, and the piston through holes 18 are also inclined in the extending direction. Extending, this ensures that the piston 23 and the second seal 16 remain attached during the encounter, ensuring a sealing effect.
  • the first sealing member 22 can be arranged as shown in FIG. 4, the outer circumference of which protrudes into a part of the annular groove, and is adhered to the groove wall to enhance the sealing effect, and the overall thickness is strengthened to improve the strength and bearing capacity. .
  • a transmission mechanism for transmitting the power of the transmission shaft 21 to the rotating shaft 17 is further provided.
  • the shaft end of the transmission shaft 21 is provided with a fourth bevel gear 35 as a driving wheel, and a fourth bevel gear. 35 drives the rotating shaft 17 to rotate by the transmission mechanism.
  • the transmission mechanism includes a second driven shaft 31.
  • the second driven shaft 31 is sleeved with a third bevel gear 32, a fourth gear 33a and a second sprocket 33b.
  • the drive shaft 21 is sleeved with a third bevel gear 32.
  • the meshing fourth bevel gear 35 has a fifth gear 36a and a first sprocket 36b respectively disposed on the two rotating shafts 17, wherein the first sprocket 36b and the second sprocket 33b pass through one
  • the chain 34 is connected, the fifth gear 36a is meshed with the fourth gear 33a, and the power of the transmission shaft 21 is passed through the fourth bevel gear 35, the third bevel gear 32, the second driven shaft 31, the fourth gear 33a, and the second chain.
  • the wheel 33b and the first sprocket 36b are transmitted to the rotating shaft 17, which drives the second sealing member 16 to rotate, and the two second sealing members 16 are rotated in opposite directions.
  • the present embodiment is different from the first embodiment in that the structure and position of the annular cylinder 11 and the transmission mechanism are different, and the rest is similar to that of the embodiment 1:
  • the cylinder block 1 and the first seal 22 are disk-shaped and coaxially juxtaposed, and the drive shaft 21 is coupled to the cylinder block 1 through bearings, in the first seal 22 and the cylinder.
  • the piston 23 and the annular groove are respectively disposed on the opposite end faces of the body 1, and the first seal 22 and the opposite end faces of the cylinder block 1 are fitted to each other to form the annular cylinder 11.
  • the drive shaft 21 is sleeved with a bearing, and the bearing is located between the cylinder block 1 and the transmission shaft 21 for better support.
  • a seventh bevel gear 55 as a driving wheel is sleeved on the driving shaft 21, and a fifth driven shaft 52 is further disposed on the outer bracket 6.
  • the fifth driven shaft 52 is sleeved with a tenth gear 53a and a third chain.
  • the wheel 53b, the eighth bevel gear 54, the eighth bevel gear 54 meshes with the seventh bevel gear 55, and the tenth gear 53a meshes with the eleventh gear 56a sleeved on one of the rotating shafts 17, and the third sprocket 53b
  • the fourth sprocket 56b sleeved with the other rotating shaft 17 is connected by the second chain 57 to transmit the power of the propeller shaft 21 to the rotating shaft 17, so that the rotation directions of the two second sealing members 16 are opposite.
  • the annular groove is formed on the end surface of the cylinder block 1.
  • the first sealing member 22 and the cylinder block 1 are fitted to form an annular cylinder 11, and the joint surface of the two can be in the form of a stepped surface.
  • FIG. 15 is a cross-sectional view after the second seal member 16 is hidden, the cylinder block 1 and the first seal member 22 are closely fitted, the piston 23 is cut away from the middle portion, and the overall projection of the piston 23 in the direction of movement thereof is annular.
  • the cylinder 11 has a fan shape having a uniform cross-sectional shape, the front portion seals the outer portion of the annular cylinder 11 and the rear portion seals the inner portion of the annular cylinder 11.
  • the second seal 16 seals the block mounting opening 15 while the piston passage 18 on the second seal 16
  • the inner wall is always attached to the outer contour of the piston 23 to ensure the sealing effect.
  • the outer circumference of the second sealing member 16 in this example is also concave, and the rest of the structure is similar to that of the first embodiment.
  • the piston 23 rotates clockwise with the first seal member 22, and the second seal member 16 located below rotates counterclockwise as viewed from the left.
  • the piston 23 moves from the intake valve 12 to the stopper mounting port, and during this movement, the suction chamber A at the rear of the piston 23 (the chamber between the piston 23 and the intake port 12) gradually becomes larger and air Intake into the suction chamber A from the intake valve 12, the compression chamber B (the chamber between the piston 23 and the second seal 16) in front of the piston 23 gradually becomes smaller and the air in the compression chamber B passes through the air guide hole 25.
  • the intake end is compressed into the gas storage chamber in the piston 23 to form a high temperature and high pressure gas; when the piston 23 moves to the upper second seal 16, the volume of the compression chamber B becomes minimum 0, and the piston 23 simultaneously compresses the chamber B
  • the air in the air is completely compressed into the gas storage combustion chamber, at which time the piston passage 18 of the upper second seal member 16 (shown in Figure 9) is also just turned to the block mounting opening 15; when the piston 23 passes through the piston
  • the outlet end of the air guiding tube 25 on the piston 23 behind the hole 18 is opened (in the process, the gas can also be pressed into the air reservoir through the air reservoir, and after the piston 23 passes through the piston through hole 18, the air outlet in front of the piston 23 is ejected.
  • the gas is supplied to the expansion chamber C), at which time the spark plug on the piston 23 is ignited, the gas is ignited, and the high-temperature high-pressure combustion gas in the gas-storage combustion chamber is injected into the expansion chamber C between the upper second seal member 16 and the piston 23.
  • the combustion gas expansion pushes the piston 23 to work in a direction away from the second sealing member 16 away from the side, during which the expansion chamber C between the second sealing member 16 and the piston 23 is gradually enlarged, while the piston 23 will be the piston 23
  • the exhaust gas in the chamber formed between the lower second seal member 16, that is, the exhaust chamber D is pushed downward toward the second seal member 16 and exhausted through the exhaust valve 14 to exhaust the exhaust gas from the exhaust valve 14.
  • the upper and lower pistons 23 are symmetrically arranged, when the square piston 23 located to the left of the upper second seal member 16 is inhaling and compressing the gas, the piston 23 located to the right of the upper second seal member 16 is performing work and exhaust. Therefore, during the rotation process, the two pistons 23 perform the process of inhaling while compressing and simultaneously performing the work of exhausting. During the whole process, the internal combustion engine rotates once to complete the work strokes of the suction, compression, expansion work and exhaust.
  • the compression ratio and the expansion ratio of the conventional reciprocating piston internal combustion engine and the triangular rotor internal combustion engine are equal, which leads to the high exhaust pressure and temperature of the exhaust gas of the conventional internal combustion engine, and a large part of the energy is not utilized, so the thermal efficiency is low.
  • the fuel consumption is high, and the triangular rotor internal combustion engine currently in use has a lower compression ratio and a shorter work stroke and time, so that the fuel is less able to fully burn and work, so the thermal efficiency is lower and the fuel consumption is higher.
  • the present internal combustion engine can increase the ratio of compression to expansion by changing the distance between the intake port 12 and the second seal member 16 so that the expansion ratio of the gas is greater than the compression ratio of the gas to improve the thermal efficiency of the internal combustion engine (equivalent to the conventional internal combustion engine).
  • the exhaust gas continues to work, so that the pressure and temperature of the exhaust gas of the internal combustion engine are lower than the temperature and pressure of the exhaust gas of the conventional internal combustion engine. Since the internal combustion engine also has a long working stroke, the thermal efficiency of the internal combustion engine is higher.
  • the internal combustion engine has no reciprocating parts, and all the moving parts are purely circular rotating motions, so the internal combustion engine has no vibration and no shaking during operation, and the conventional internal combustion engine has a large number of reciprocating pistons, crankshafts, connecting rods, etc. Moving parts have violent vibrations and jitter that cannot be eliminated while working. Even the triangular rotor internal combustion engine is incapable of eliminating vibration and vibration because the piston is not purely circular.
  • the internal combustion engine has no crankshaft, connecting rod, piston ring and complicated valve supporting mechanism, so the structure of the internal combustion engine is simpler and smaller, the noise is lower during operation, the processing and manufacturing are more convenient, and the cost is lower.
  • crankshafts, connecting rods, pistons and other components are squeezed from each other during operation. Therefore, a large amount of lubricating oil and a complicated lubrication system are required to ensure normal operation between the various components, even if a large amount of lubricating oil is used. Lubrication
  • the crankshaft, connecting rod, piston, piston ring, and particularly the cylinder block of the reciprocating piston internal combustion engine are also severely worn, resulting in air leakage and greatly shortened service life.
  • the internal combustion engine only needs lubrication between the gears, and the piston, the cylinder body and the sealing member do not need a sealing ring like a piston ring, and only the contact between them is not pressed, so there is almost no friction and the sealing effect is better. Therefore, the internal combustion engine has better airtightness and less wear, and the energy lost by friction is smaller and the service life is longer.
  • the triangular rotor internal combustion engine has a high sealing effect due to irregularities of the cylinder block and the piston, and is difficult to manufacture and maintain, and is costly.
  • the internal combustion engine has higher working efficiency, higher thermal efficiency, minimum fuel consumption, the simplest structure, the fastest and smoothest operation, and the noise. Minimal, minimum friction, best sealing effect, minimum mechanical energy loss, lowest cost, more convenient maintenance and longest service life.
  • a rotary piston type working machine includes two disc-shaped cylinder blocks 1 coaxially juxtaposed, and an annular groove is formed in each of the two cylinder blocks 1, and an annular groove of the two cylinder blocks 1 is provided.
  • the openings are opposite to each other, and the first sealing member 22 is interposed between the two cylinder blocks 1.
  • the two annular grooves are fitted to the end faces of the first sealing member 22 to form two annular annular cylinders 11 respectively.
  • the drive shaft 21 is mounted on the axis of the cylinder block 1 by bearings and is fixedly coupled to the first seal 22; a piston 23 is disposed on the first seal 22 in the annular cylinder 11, the piston 23 and the annular cylinder 11 adaptation.
  • the cylinder block 1 is provided with a stopper mounting opening 15 extending transversely to the annular cylinder 11 , and the two cylinder blocks 1 are adjacent to the stopper mounting opening 15 formed on the same side to form a pair of stopper mounting openings, outside the cylinder block 1
  • the second seal member 16 supported by the rotary shaft 17 projects into the stopper mounting opening 15, and the steering of the pair of second seal members 16 on the same side of the cylinder block 1 is the same.
  • the end surface of the first sealing member 22 is provided with a second annular groove 221 corresponding to the annular groove, and the groove bottom of the second annular groove 221 has a circular arc shape.
  • the second sealing member 16 has a disk shape with a large end and a small end, and the end faces of the second sealing member are close to each other (as shown in FIG. 19).
  • the second sealing member 16 is provided with at least one piston through hole 18, the piston 23 rotates around the transmission shaft 21 and moves circumferentially along the annular cylinder 11, and the second sealing member 16 rotates around the rotating shaft 17,
  • the second sealing member 16 is rotated to a position corresponding to the piston through hole 18 and the piston 23, so that the piston 23 just passes through the piston through hole 18, and the second
  • the seal 16 seals the chambers on both sides of the stopper mounting opening 15 and the stopper mounting opening 15 during movement.
  • the two cylinder blocks 1 are the first cylinder block 1a on the right side and the second cylinder block 1b on the left side, respectively, and the first cylinder block 1a and the second cylinder block 1b are respectively coupled to the first seal member.
  • 22 constitutes a first annular cylinder 11a and a second annular cylinder 11b, and the second seal 16 and the piston 23 divide each annular cylinder 11 into two chambers.
  • the annular cylinder 11 on both sides of the stopper mounting opening 15 is provided with an intake port 12 and an air outlet 14 respectively, and a passage for connecting the two annular cylinders 11 is provided between the pair of stopper mounting openings 15.
  • the passage includes a gas storage combustion chamber 37 and an associated gas injection passage 38, and a gas storage combustion chamber 37 A spark plug 39 or a fuel injector is disposed, and the air outlet 14 of the first annular cylinder 11a is connected to the air reservoir 37 through the air reservoir check valve 44, and the air outlet of the air passage 38 is the second annular cylinder 11b. Air port.
  • the gas storage combustion chamber 37 serves as a combustion chamber, and does not require the use of a long-path air guiding tube from outside the cylinder body, and does not require an externally-operated jet control valve, which simplifies the structure; and does not require the combustion chamber to be disposed inside the piston 23, It also simplifies the structure and reduces the difficulty of implementing the control valve.
  • the jet passage 38 is disposed on the first seal member 22, and the jet passage 38 on the first seal member 22 conducts the gas storage combustion chamber 37 and the second annular cylinder 11b at the end of the compression stroke to the end of the expansion work stroke. .
  • the gas injection passage 38 includes a sector groove 222 provided on the first sealing member 22, which is fan-shaped.
  • the slot of the slot 222 is defined in the middle of the outer circumferential surface of the first sealing member 22.
  • a jet opening communicating with the fan-shaped slot 222 is opened, at the end of the compression stroke.
  • the gas injection passage 38 of the first seal member 22 conducts the gas storage combustion chamber 37 and the second annular cylinder 11b, and the first seal member 22 is further provided with a seal ring for sealing the outer circumference of the sector groove 222. 40.
  • the sealing ring 40 is provided with a radial through hole 401, and the through hole 401 is in communication with the gas storage combustion chamber 37.
  • the air passage 38 may be turned on or off by the rotating first seal 22, and the air passage 38 is turned on when the inlet of the air passage 38 is opposed to the outlet of the air reservoir 37.
  • the seal ring may be a separate component or may be provided as a unitary structure with the cylinder block.
  • the air vents in this embodiment are provided with three, one main air vent 41 and two sub air vents 42, and the sub air vent 42 is located at the main jet in the direction of rotation of the first seal 22.
  • the air inlet port 42 is provided with a gas jet port check valve 43. Only when the pressure in the gas storage combustion chamber 37 exceeds the spring force of the gas jet port check valve 43, the valve can be pushed open to allow the gas to enter the first stage.
  • the two annular cylinders 11b if the secondary air outlets 42 are not rotated into the expansion chamber C, the gas pressure in the air storage combustion chamber 37 will be insufficient to push the air outlet check valve 43 and deflate through the secondary air outlet 42, for the purpose of multiple air intake.
  • a plurality of gases are introduced into the passage of the expansion chamber C to achieve rapid expansion work, and a plurality of air ports are provided.
  • the intake port 12 of the first annular cylinder 11a and the air outlet 14 of the second annular cylinder 11b are respectively connected to the intake pipe and the exhaust pipe, the intake compression is completed by the first annular cylinder 11a, and the second annular cylinder 11b completes the work discharge gas.
  • the shaft end of the transmission shaft 21 is provided with a sprocket as a driving wheel, and the driving wheel drives the rotating shaft 17 to rotate through a transmission mechanism 48, and the transmission mechanism 48 includes a sprocket chain pair and a bevel gear pair.
  • the pair of second seals 16 on the same side rotate in the same direction.
  • the structure and working principle of the technical solution are basically the same as those of the first embodiment, except that the two annular cylinders 11 are juxtaposed, the suction and compression are completed by the first annular cylinder 11a, and the expansion and the work are completed by the second annular cylinder 11b.
  • the cylinders are arranged side by side and divided. Compared with the foregoing first technical solution, the better effects are as follows: 1. The cost can be reduced and the performance can be improved; 2. The gas enters the expansion chamber C from the compression chamber B. It is easy to implement technically, which can reduce technical difficulty and reduce manufacturing and maintenance costs, simplify structure and increase work stability. 3.
  • the combustion chamber The second sealing member 16 and the piston 23 must have good sealing on both sides, which is required in the material selection and manufacturing process.
  • the degree of sealing on both sides of the second sealing member 16 and the piston 23 only needs to ensure that one side has a stable and good sealing property (one side of the compressed gas or a side on which the gas expands), so that the existing material and technology are available. It can be easily realized; 4.
  • the gas's work stroke is twice that of the first technical solution, and the combustion and work are completed completely, which can improve the efficiency and reduce the cost of the fuel.
  • this embodiment is basically the same as Embodiment 3, except that the air injection passage 38 is disposed on the second cylinder block 1b of the second annular cylinder 11b, and the air passage 38 and the second ring are provided.
  • the cylinder 11b is in communication, and an openable and closable gas injection valve 45 is provided at an exit position of the gas storage combustion chamber 37, and the jet valve 45 is opened at the end of the compression stroke to the end of the expansion power stroke.
  • the jet valve 45 is a rotary valve whose valve plate is semi-circular. When the compression stroke is performed, the semicircular portion of the valve plate blocks the outlet of the gas storage combustion chamber 37, and the end of the compression stroke is about to be ignited until the end of the compression stroke. At the end of the expansion work stroke, the valve piece is opened, and the gas in the gas storage combustion chamber 37 can enter the expansion chamber C through the gas passage 38 on the second cylinder block 1b.
  • this embodiment is basically the same as Embodiment 3 except that a double piston is used to obtain better dynamic balance, and the working machine runs more smoothly.
  • the gas storage combustion chamber 37, the gas passage, the gas jet, the piston 23 and the second seal 16 are two sets.
  • Each of the cylinder blocks 1 is provided with two stopper mounting openings 15 which are 180 degrees symmetric.
  • the two stopper mounting openings 15 are elongated and arranged in parallel, and the two second sealing members 16 are small discs having one end and a small end.
  • the large end surface 16a of the second sealing member 16 is located on a plane passing through the axis of the transmission shaft 21; the first sealing member 22 is provided with two pistons 23 which are 180 degrees symmetric, two pistons 23 and two
  • the second sealing member 16 divides the annular cylinder 11 into four chambers.
  • the two annular block mounting openings 15 of the first annular cylinder 11a are provided with an air inlet 12 and an air outlet 14, that is, a first annular cylinder 11a.
  • Two air inlets 12 and two air outlets 14 are disposed, and the air inlet 12 and the air outlet 14 are spaced apart.
  • the air outlet 14 of the first annular cylinder 11a passes through the air storage combustion chamber 37 and the air passage 38 and the second.
  • the intake port of the annular cylinder 11b is connected, and the second annular cylinder 11b is provided with two air outlets 14 respectively communicating with the exhaust pipe.
  • a coolant passage 223 that is connected to the cooling hole in the transmission shaft 21 is disposed in the first seal 22 as shown in FIGS. 34, 37, and 38, and the coolant passage 223 will be
  • the outer circumference of the first seal member 22 is penetrated, and a coolant passage 1c (only the first cylinder block 1a is illustrated) is also disposed in the two annular cylinder bodies.
  • the structure of the gas storage combustion chamber 37, the gas passage, the gas jet, the piston 23, and the sector groove 222 is the same as that of the third embodiment, and the structure of the fourth embodiment can also be employed for the gas passage.
  • the seal ring 40 of the embodiment 3 is integrally formed with the first cylinder block 1a, and the first cylinder block 1a is provided with a through hole 401 communicating with the gas storage combustion chamber, the first seal.
  • the driving shaft 21 is provided with a driving bevel gear 49.
  • the driving bevel gear 49 meshes with the driven bevel gear 50, and then the four rotating shafts 17 are rotated by the transmission mechanism 48, and the transmission mechanism 48 includes many Engaged gears.
  • this embodiment is basically the same as Embodiment 5 except that the passage connecting the two annular cylinders is not a gas storage combustion chamber and a gas passage, but only the first annular cylinder 11a and the second.
  • the air outlet 14 of the annular cylinder 11b is connected to the exhaust pipe 47 by a three-way pipe 46, and can be used as an air compressor.
  • An air inlet 12 and an air outlet 14 are respectively disposed on the cylinder walls on both sides of each of the stopper mounting ports 15.
  • the inlet and outlet ports 12 and 14 are alternately distributed along the cylinder circumferential direction, and the air outlet 14 communicates with the exhaust pipe.
  • the two second seals 16 on the same side rotate in opposite directions.
  • the power is driven by the drive shaft 21 to drive the piston 23 to compress the gas.
  • Each annular cylinder can be provided with two pistons 23 and two block mounting ports 15, and the gas is compressed and discharged from the air outlet 14 through the exhaust pipe to the external storage.
  • the piston 23 can rotate more than one turn to compress more gas, so that the compression efficiency is improved.
  • Fig. 39 shows the air compressor in the case of a single piston structure.
  • the principle of the working machine can also be used to convert into an air extractor or a liquid pumping machine.

Abstract

旋转活塞式工作机，包括气缸体（1）和传动轴（21）。气缸体（1）上开设有一圈环形槽，传动轴（21）上连接的第一密封件（22）将环形槽密封，并与气缸体围成密闭的环形气缸；环形气缸内设有至少一个活塞（23），气缸体（1）上开有至少一个挡块安装口（15），挡块安装口（15）内安装有由转轴支撑的第二密封件（16）；第二密封件（16）上开设有至少活塞过孔，在活塞（23）刚好转动至第二密封件（16）时，第二密封件（16）转动至活塞过孔与活塞（23）对应的位置，使活塞（23）刚好通过活塞过孔，第二密封件（16）在运动过程中将挡块安装口（15）以及两边的腔室密封。本发明工作机减少能量损失与摩擦，寿命长，压缩比大，做功效率高，燃烧充分，排污少，节能环保。

Description

旋转活塞式工作机 技术领域
本发明属于内燃机或空气压缩技术领域，特别涉及一种旋转活塞式工作机。
背景技术
目前普遍使用的是往复活塞式内燃机，活塞在缸体中往复直线运动，通过曲柄连杆机构将活塞的直线运动转变为旋转运动作为动力输出，其结构复杂、所占空间大、运动部件多，非圆周运动的零部件之间摩擦大，不但制造成本高、容易坏损，还因往复惯性力的周期性变化使得发动机不平衡，造成振动引起噪声，能量消耗，连接件松动，磨损严重而缩短使用寿命等问题，影响内燃机的平顺性、舒适性和可靠性，只能增加平衡块等平衡件进行有限平衡，但使得内燃机结构进一步复杂化。即使是目前在应用的三角转子内燃机也不是纯圆周运动且三角转子内燃机的压缩比小热效率低，还有三角转子内燃机因为气缸体和活塞的不规则导致其密封效果差以及制造和维修困难而成本高。此外，更重要的是往复活塞式四冲程内燃机曲轴旋转两周才能完成一个工作循环做功一次，即使是二冲程内燃机完成一次做功也需要曲轴旋转一周，其做功不连续，不但效率低，动力输出也不平稳。所以无论是往复活塞内燃机还是三角转子内燃机都无法同时满足运转平稳、做功连续、极高转速、噪音小、摩擦小、润滑油需求量小、使用寿命长、功率和热效率高、结构简单、制造和维修容易等要求。
发明内容
鉴于以上所述现有技术的缺点，本发明的目的在于提供一种旋转活塞式工作机，结构更为简单，改变传统活塞往复运动做功为旋转运动做功或压缩气体，转速更快，效率更高，做功运行更平稳，使用寿命更长。
为实现上述目的及其他相关目的，本发明提供一种旋转活塞式工作机，包括环状或盘状的气缸体，所述气缸体上沿气缸体的周向开设有一圈环形槽，所述气缸体轴线上设置有传动轴，该传动轴上连接有第一密封件，所述第一密封件将所述环形槽密封，并与所述气缸体围成密闭的环形气缸，在环形气缸内的所述第一密封件上设置有至少一个活塞，所述活塞与环形气缸适配；所述气缸体上沿周向开设有至少一个挡块安装口，在气缸体外部由转轴支撑的第二密封件伸入所述挡块安装口，第二密封件与所述活塞将所述环形气缸分隔为至少两个腔 室，所述第二密封件上开设有至少一个活塞过孔，所述活塞绕传动轴旋转，并沿环形气缸做周向运动，所述第二密封件绕转轴旋转，在所述活塞转动至第二密封件时，所述第二密封件转动至活塞过孔与活塞对应的位置，使活塞刚好通过所述活塞过孔，且所述第二密封件在运动过程中将所述挡块安装口以及挡块安装口两边的腔室密封，所述气缸体上设有进气口和出气口。
采用上述结构当只有一个挡块安装口两侧的气缸壁上分别设有进气口和出气口时，该机体可以用作内燃机机体，活塞与第一密封件固连，也可以为一体成型，通过第一密封件带动传动轴转动，从而使传动轴直接输出扭矩，减少了传动过程中因为摩擦或者传动部件过多而带来的能量损失，由于改变原往复运动的方式为旋转运动，活塞可以为多个对称设置，使得该内燃机运转十分平稳，而且能够达到更高的转速，出气口和进气口的位置根据需求可以适当改变，以调整输出功率。本结构不存在往复活塞式内燃机的活塞对气缸壁的偏心压力，因而本发明在气缸体和密封件之间只有接触没有挤压所以几乎没有摩擦，这样既能减少因为摩擦而损失能量又能延长零部件的使用寿命。而且动平衡好，不存在传统内燃机因往复惯性力的周期性变化使得发动机不平衡，造成振动引起噪声，能量消耗，连接件松动，磨损严重而缩短使用寿命等问题，内燃机振动、噪声小，平顺性和可靠性高。
当每个挡块安装口两侧的气缸壁上均分别设置出气口和进气口时，可以用作空压机使用，动力经传动轴接入驱动活塞运动，压缩气体，此时可以设置多个活塞和多个挡块安装口，气体经压缩后从出气口排入外部储气罐，由于气缸体内腔较大，活塞旋转一圈能够压缩更多气体，使压缩效率提高。
上述技术方案的有益效果是：两个活塞和两个第二密封件将环形活塞腔分隔成吸气室、压缩室、膨胀室、排气室四个腔(当采用双活塞时)，活塞在环形活塞腔内转动，整个过程中内燃机旋转一次能够完成吸气、压缩、膨胀做功和排气的工作冲程两次，并且是不间断地连续进行，相当于同样排气量的往复式内燃机功率的几倍。通过第一密封件带动传动轴转动，从而使传动轴直接输出扭矩，减少了传动过程中因为摩擦或者传动部件过多而带来的能量损失；由于改变原往复运动的方式为旋转运动，活塞对称设置，没有传统的往复运动式内燃机振动剧烈，使得该内燃机运转十分平稳，而且因为所有运动部件为纯圆周旋转运动所以本内燃机能够平稳无振动地达到理想高的转速；出气口和进气口的位置根据需求可以适当改变，以调整输出功率达到比传统内燃机更高的热效率。该结构由于活塞、气缸和密封件之间只有接触没有挤压所以几乎没有摩擦，这样既能减少因为摩擦而损失能量又能延长零部件的使用寿命。
本发明还提供了一种旋转活塞式工作机，包括同轴并列的盘状的两个气缸体，两气缸体上分别开设有一圈环形槽，两气缸体的环形槽开口相向，两所述气缸体之间夹装有第一密封件，两环形槽与第一密封件的两侧贴合而分别形成密闭的两个环形气缸，传动轴通过轴承安装在气缸体轴线上并且与第一密封件固定连接；在每个环形气缸内的所述第一密封件上设置有至少一个活塞，所述活塞与环形气缸适配；
所述气缸体上至少开设有一个横向连通环形气缸的挡块安装口，两气缸体同侧的挡块安装口相邻而组成一对挡块安装口，在气缸体外部由转轴支撑的第二密封件伸入所述挡块安装口，第二密封件与所述活塞将每个所述环形气缸分隔为至少两个腔室，所述第二密封件上开设有至少一个活塞过孔，所述活塞绕传动轴旋转，并沿环形气缸做周向运动，所述第二密封件绕转轴旋转，在所述活塞转动至第二密封件时，所述第二密封件转动至活塞过孔与活塞对应的位置，使活塞刚好通过所述活塞过孔，且所述第二密封件在运动过程中将所述挡块安装口以及挡块安装口两边的腔室密封；每个挡块安装口两侧的环形气缸上分别设置有进气口和出气口，在每对挡块安装口旁侧设置有将两环形气缸连通的通道。
本技术方案为两个并列的环形气缸，吸气和压缩由第一环形气缸完成，而膨胀和做功由第二环形气缸完成，两个气缸并列设置并分工，其相较于前述第一个技术方案而言，其更优的效果在于：1、在同样排量的情况下，活塞和密封盘以及配套的结构只需要第一个技术方案的一半，这样大大简化结构，降低成本和增加性能的稳定性；2、气体从压缩室进入膨胀室容易从技术上实现，这样既能降低技术难度又能降低制造和维修成本，更能简化结构和增大工作的稳定性；3、第一技术方案中，燃烧室处的第二密封件与活塞必须要两侧都具有很好的密封性，在选材和制作工艺上要求较高，而本技术方案中，当活塞穿过第二密封件时，第二密封件和活塞两侧的密封程度只需要保证一侧具有稳定和良好的密封性即可(压缩气体的一侧或者气体膨胀的一侧)，这样从现有的材质和技术上都能容易实现。
附图说明
图1为本发明实施例1的结构示意图。
图2为图1的左视图。
图3为图1中气缸体与第一、第二密封件配合的结构示意图。
图4为图3中的气缸体与第一密封件配合的剖视图。
图5为第二密封件、活塞与第一密封件的配合结构示意图。
图6为实施例1中活塞的结构示意图。
图7为图6中导气孔进气端单向阀的结构示意图。
图8为图6中导气孔出气端单向阀的结构示意图。
图9为图1中第二密封件与气缸体和第一密封件配合的结构示意图。
图10为第一密封件、活塞和第二密封件的配合关系示意图。
图11为实施例1第二密封件的结构示意图(仅示出一个活塞过孔)。
图12为本发明实施例2的结构示意图。
图13为图12的右视图。
图14为本发明实施例2中环形气缸的结构示意图。
图15为本发明实施例2中环形气缸和活塞的配合关系示意图。
图16为图15中增加第二密封件后的配合关系图。
图17为图16中左视方向的剖视图(气缸体未示出)。
图18为本发明实施例3结构示意图。
图19为图18的右视图。
图20为图18中环形气缸和贮气室的剖视结构示意图(喷气通道导通膨胀室时)。
图21为图18的F-F剖视结构示意图。
图22为图18的G-G剖视结构示意图。
图23为本发明实施例3环形气缸和活塞的配合关系剖视图。
图24为图23中第一气缸体的结构示意图。
图25为图20的H-H剖视结构示意图。
图26为实施例3中密封环的结构示意图。
图27为实施例3中第一密封件的结构示意图。
图28为图27中副喷气口位置的剖视结构示意图。
图29为本发明实施例4的结构示意图。
图30为图29中喷气阀的阀片的结构示意图。
图31为本发明实施例5局部剖视的结构示意图。
图32为图31的仰视图(加上了贮气燃烧室)。
图33为图32的右视图。
图34为图31中第一环形气缸的剖视结构示意图。
图35为实施例5第一环形气缸的配气示意图(图31的右视方向)。
图36为实施例5第二环形气缸的配气示意图(图31的左视方向)。
图37为图31中第一密封件的立体图。
图38为图31中第一密封件的横剖结构示意图。
图39为本发明实施例6一种实施方式的结构示意图。
图40为本发明实施例6另一种实施方式的结构示意图。
图41为图40中活塞穿过第二密封件时的剖视结构示意图(右视方向)。
具体实施方式
以下通过具体实施例说明本发明的实施方式。
实施例1：
如图1至图11所示，本发明提供一种旋转活塞式工作机，本例中旋转活塞式工作机用于内燃机，包括环状的气缸体1，气缸体1内沿气缸体1的周向开设有一圈环形槽，气缸体1的轴线上设置有传动轴21，传动轴21设置在气缸体1内圈中心，该传动轴21上连接有第一密封件22，所述第一密封件22将所述环形槽密封，并与所述气缸体1围成密闭的环形气缸11。第一密封件22为圆盘形，其圆盘外圆周中间高两侧低，第一密封件22的外圆周中间部分伸入环形槽与活塞23连接，并将环形槽密封，与气缸体1共同围成环形气缸11。该环形气缸11内的第一密封件22上设置有两个活塞23，活塞23与环形气缸11适配，第一密封件22外圆周的低处与气缸体1内圈的外壁贴合，第一密封件22始终将环形槽槽口密封，两个活塞23相对于传动轴21对称设置，该气缸体1侧壁上设有进气口12、出气口14。
为了使结构紧凑，并且实现第二密封件16与第一密封件22达到完全适配，所述第二密封件16为圆盘状，两个第二密封件16的外周部伸入所述挡块安装口内。如图3所示，该第二密封件16外圆周内凹并且与第一密封件22的外圆周所接触的部分适配，第二密封件16外圆周与第一密封件22相接触，第二密封件22对称开有两个活塞过孔，所述第一密封件16位于环形气缸的部分内凹，两个所述第二密封件22由传动机构带动而相反向地旋转。
气缸体1上沿周向开设有两个挡块安装口15，每个挡块安装口15内插装有一个第二密封件16，该第二密封件16在气缸体外部由转轴支撑，第二密封件16的外周部伸入所述挡块安装口，第二密封件16与活塞23将环形气缸11分隔为四个腔室。转轴17安装在外部支架6上，两个转轴17和两个第二密封件16设置于气缸体1外侧，第二密封件16为圆盘状。如图3和图4所示，该第二密封件16和第一密封件22的外圆周母线的中间部分均内凹且相互适配，该结构可以使第二密封件16的外圆周和第一密封件22外圆周在转动过程中保持贴合，实现密封；活塞过孔18为两个，180度对称地开设在第二密封件16上；内燃机工作时，活 塞23随第一密封件22绕传动轴21旋转，并沿环形气缸11做周向运动，第二密封件16绕转轴17旋转，该转轴17与传动轴21垂直交错，在活塞23转动至第二密封件16时，第二密封件16转动至活塞过孔18与活塞23对应的位置，使活塞23刚好通过活塞过孔18，且第二密封件16在运动过程中将挡块安装口15密封，第二密封件16在运动过程中，将所述挡块安装口15以及挡块安装口15两侧的腔室密封。
如图3所示，其中一个挡块安装口15两侧的气缸壁上分别设有进气口12和出气口15，另一个挡块安装口15两侧的气缸壁上分别开设有贮气口和喷气口，该贮气口和喷气口通过贮气管连接(未图示)，该贮气口和喷气口分别设置有一个密封阀，用于开启和关闭贮气口和喷气口，贮气口和喷气口之间设有贮气燃烧室，贮气燃烧室中设有火花塞或喷油嘴，该结构属于现有技术(参见公告号为CN101684745A的中国发明专利申请公开文献)，在此不再赘述。
当然，也可以是如图6至图8所示，在活塞23上设置有导气孔25，导气孔25沿活塞23的长度方向延伸并贯通活塞23的前后部，该导气孔25的前后端均设置有一个单向阀，两个单向阀打开方向一致，两个单向阀之间的导气孔25形成贮气燃烧室，单向阀可以在不同的压力临界值时打开，图7和图8分别示出导气孔25的进、出气端的单向阀26a、26b，其采用弹簧连接梯形阀门的结构。
如图6、图9至图11所示，所述第二密封件16的活塞过孔18的形状与所述活塞23的形状对应，所述活塞23的前、后侧面是倾斜延伸的螺旋形曲面，活塞23的左、右侧面与环形气缸11的左右侧壁贴合，在传动轴21轴线所在平面的投影上，所述活塞23的形状呈扇形，所述活塞过孔18为扇形孔，在活塞23和第二密封件16相遇的过程中，所述活塞过孔18的内壁与活塞23外轮廓面保持贴合。这种活塞结构，使得活塞23的前、后侧面是沿活塞长度方向倾斜延伸的具有一定扭曲度的螺旋形曲面，与之相适配地，活塞过孔18在延伸方向上也为倾斜的曲线延伸，这样能够保证活塞23和第二密封件16在相遇过程中一直保持贴合，保证密封效果。
本例中第一密封件22可以设置成如图4所示的结构，其外圆周伸入环形槽一部分，并与槽壁贴合增强密封效果，整体厚度有所加强，提高其强度和承载力。
从图1和图2可以看到，还设置有将传动轴21的动力传到转轴17上的传动机构，传动轴21的轴端设置有作为驱动轮的第四锥齿轮35，第四锥齿轮35通过传动机构带动转轴17旋转。传动机构包括第二从动轴31，该第二从动轴31上套有第三锥齿轮32、第四齿轮33a和第二链轮33b，传动轴21上套有一个与第三锥齿轮32啮合的第四锥齿轮35，两根转轴17上分别套有一个第五齿轮36a和第一链轮36b，其中第一链轮36b与第二链轮33b通过一根 链条34连接，第五齿轮36a与第四齿轮33a啮合，所述传动轴21的动力经第四锥齿轮35、第三锥齿轮32、第二从动轴31、第四齿轮33a、第二链轮33b、第一链轮36b传到转轴17，带动所述第二密封件16转动，并使得两个第二密封件16的转动方向相反。
实施例2：
如图12至图17所示，本实施例与实施例1不同之处在于环形气缸11的结构和位置以及传动机构不同，其余与实施例1类似：
请参见图12至图16，气缸体1和第一密封件22呈盘状并且同轴并列对置，所述传动轴21通过轴承与气缸体1连接，在所述第一密封件22和气缸体1相对置的端面上分别设置所述活塞23和环形槽，第一密封件22和气缸体1相对置的端面贴合而形成所述环形气缸11。传动轴21上套有轴承，该轴承位于气缸体1与传动轴21之间，起更好的支撑作用。传动轴21上套接有作为驱动轮的第七锥齿轮55，外部支架6上还设置有一根第五从动轴52，该第五从动轴52上套有第十齿轮53a、第三链轮53b、第八锥齿轮54，所述第八锥齿轮54与第七锥齿轮55啮合，第十齿轮53a与其中一根转轴17上套设的第十一齿轮56a啮合，第三链轮53b与另一根转轴17上套设的第四链轮56b通过第二链条57连接，以将传动轴21的动力传至转轴17，使得两个第二密封件16的转动方向相反。
如图14至图17所示，本实施例中环形槽开设在气缸体1端面，第一密封件22和气缸体1贴合围成环形气缸11，两者的结合面可以采用阶梯面的形式实现多重密封，其中图15为隐藏第二密封件16后的剖视图，气缸体1和第一密封件22紧密配合，活塞23从中部剖开，活塞23在其运动方向上的整体投影呈与环形气缸11的横截面大小一致的扇形，前部将环形气缸11靠外侧部分密封，后部将环形气缸11靠内侧部分密封。如图16和图17所示，活塞23在与第二密封件16相遇的过程中，第二密封件16在封住挡块安装口15的同时，第二密封件16上的活塞过孔18内壁始终与活塞23外轮廓贴合，保证其密封效果，本例中的第二密封件16外圆周也内凹，其余结构跟实施例1相类似。
下面以实施例1为例阐述旋转活塞式工作机用作内燃机的工作原理：
如图3所示，活塞23随着第一密封件22作顺时针旋转，从左看，位于下方的第二密封件16作逆时针转动。活塞23从进气门12向挡块安装口移动，在这移动的过程中，活塞23后部的吸气室A(活塞23和进气口12之间的腔室)逐渐变大并将空气从进气门12吸入到吸气室A中，活塞23前面的压缩室B(活塞23和第二密封件16之间的腔室)逐渐变小并将压缩室B中的空气通过导气孔25的进气端压缩到活塞23中的贮气燃烧室形成高温高压气体；当活塞23移动到上第二密封件16处时压缩室B的体积变为最小0，活塞23同时将压缩室B 中的空气完全压缩到贮气燃烧室中，这时上第二密封件16的活塞过孔18(如图9所示)也刚好转到挡块安装口15处；当活塞23穿过活塞过孔18后活塞23上的导气管25的出气端打开(该过程中也可以将气体通过贮气口压入贮气管，在活塞23穿过活塞过孔18后，位于活塞23前方的喷气口喷出气体至膨胀室C)，此时活塞23上的火花塞点火，燃气被点燃，贮气燃烧室中的高温高压的燃烧气体喷入到上第二密封件16与活塞23之间的膨胀室C中，燃烧气体膨胀推动活塞23向远离方的第二密封件16的方向移动而做功，在这过程中第二密封件16与活塞23之间的膨胀室C逐渐变大，同时活塞23将活塞23与下方第二密封件16之间形成的腔室即排气室D中的尾气向下方的第二密封件16推动并通过排气门14将做功完毕的尾气从排气门14排出。
由于上、下活塞23是对称布置，当位于上方第二密封件16左方的方活塞23在进行吸气和压缩气体时，位于上方第二密封件16右方的活塞23便在进行做功和排气。所以两个活塞23在旋转的过程中循环轮流进行吸气同时压缩与做功同时排气的过程，整个过程中内燃机旋转一次能够完成吸气、压缩、膨胀做功和排气的工作冲程两次。
本内燃机的优点：
传统的往复活塞内燃机以及三角转子内燃机的压缩比和膨胀比值是相等的，这导致了传统的内燃机的尾气还有很高的压强和温度而还有很大一部分的能量没有得到利用因此热效率低而油耗高，目前在应用的三角转子内燃机由于压缩比小和做功行程与时间短导致燃料更不能充分燃烧做功所以热效率更低油耗更高。本内燃机能够通过改变进气口12到第二密封件16的距离而改变压缩与膨胀的比值从而使气体的膨胀比大于气体的压缩比而提高内燃机的热效率(相当于在传统的内燃机的基础上尾气还在继续做功，这样本内燃机的尾气的压强和温度比传统的内燃机的尾气的温度和压强要低)，由于本内燃机还具有做功行程长所以本内燃机的热效率更高。
本内燃机没有往复运动的零部件，而且所有运动部件都是作纯圆周旋转运动，所以本内燃机在工作时没有振动更没有抖动的现象，而传统的内燃机因为存在活塞、曲轴、连杆等大量往复运动的部件所以工作时存在不可消除的剧烈振动和抖动。即使是三角转子内燃机因为活塞也不是纯圆周运动所以振动和抖动也是不可消除的。
本内燃机没有曲轴、连杆、活塞环以及复杂的气门配套机构等所以本内燃机的结构更为简单体积更小，运转时噪音更低，加工制造更为方便，成本更低。
传统的内燃机曲轴、连杆以及活塞等部件运转时相互之间的挤压很大所以需要大量的润滑油和复杂的润滑系统才能保证各个零部件之间能正常运转，即使这样用大量的润滑油润滑 往复活塞内燃机的曲轴、连杆、活塞、活塞环特别是气缸体也会严重磨损而导致漏气以及使用寿命大大缩短。而本内燃机只有齿轮之间需要润滑，而活塞、缸体和密封件之间既不需要类似活塞环之类的密封环而且相互之间只有接触没有挤压所以几乎没有摩擦且密封效果更好，所以本内燃机密闭性更好，磨损更小，因摩擦损失的能量更小，使用寿命更长。
三角转子内燃机因为气缸体和活塞的不规则导致其密封效果差以及制造和维修困难而成本高。
综上所述，本内燃机与传统的往复活塞内燃机以及三角转子内燃机相比，三者之中本内燃机的工作效率更大，热效率更高，油耗最小，结构最简单，运转最快最平稳、噪音最小，摩擦最小、密封效果最好、机械能损失最小，造价最低，维修更方便，使用寿命最长等优点。
实施例3：
如图18至图28所示，一种旋转活塞式工作机，包括同轴并列的两个盘状的气缸体1，两气缸体1上分别开设有一圈环形槽，两气缸体1的环形槽开口相向，两所述气缸体1之间夹装有第一密封件22，两环形槽与第一密封件22的两侧端面贴合而分别形成密闭的两个环形气缸11。传动轴21通过轴承安装在气缸体1轴线上并且与第一密封件22固定连接；在环形气缸11内的所述第一密封件22上设置有一个活塞23，所述活塞23与环形气缸11适配。
所述气缸体1上开设有一个横向连通环形气缸11的挡块安装口15，两气缸体1同侧开设的挡块安装口15相邻而组成一对挡块安装口，在气缸体1外部由转轴17支撑的第二密封件16伸入所述挡块安装口15，气缸体1同侧的一对第二密封件16的转向相同。为利用有限的体积提升环形气缸的容量，第一密封件22的端面上设置有与所述环形槽相对应的第二环形槽221，第二环形槽221的槽底为圆弧形，所述第二密封件16为一端大一端小的圆盘形，第二密封件的大端端面相靠近(如图19所示)。所述第二密封件16上开设有至少一个活塞过孔18，所述活塞23绕传动轴21旋转，并沿环形气缸11做周向运动，所述第二密封件16绕转轴17旋转，在所述活塞23转动至第二密封件16时，所述第二密封件16转动至活塞过孔18与活塞23对应的位置，使活塞23刚好通过所述活塞过孔18，且所述第二密封件16在运动过程中将所述挡块安装口15以及挡块安装口15两边的腔室密封。
如图19至图24所示，两气缸体1分别为右侧的第一气缸体1a和左侧的第二气缸体1b，第一气缸体1a和第二气缸体1b分别与第一密封件22组成第一环形气缸11a和第二环形气缸11b，第二密封件16与活塞23将每个环形气缸11分隔为两个腔室。挡块安装口15两侧的环形气缸11上分别设置有进气口12和出气口14，在一对挡块安装口15之间设置有将两环形气缸11连通的通道。所述通道包括贮气燃烧室37和相连接的喷气通道38，贮气燃烧室37 中设置有火花塞39或喷油嘴，第一环形气缸11a的出气口14通过贮气室单向阀44与贮气燃烧室37相接，喷气通道38的喷气口为第二环形气缸11b的进气口。贮气燃烧室37作为燃烧室，不需要从缸体外使用长路径的导气管，也不需要外界操控的喷气控制阀，简化了结构；并且，也不用将燃烧室设置在活塞23内部，同样，也简化了结构，降低了控制阀的实现难度。
所述喷气通道38设置在第一密封件22上，在压缩冲程末期至膨胀作功冲程结束时，第一密封件22上的喷气通道38将贮气燃烧室37和第二环形气缸11b导通。为可靠地实现贮气燃烧室37与第二环形气缸11b膨胀室C的连通，如图25至图28所示，所述喷气通道38包括设置在第一密封件22上的扇形槽222，扇形槽222的槽口开设在第一密封件22外圆表面的中部，在与第二环形气缸11b相对应的第一密封件22表面上开设有连通扇形槽222的喷气口，在压缩冲程末期至膨胀作功冲程结束时，第一密封件22的喷气通道38将贮气燃烧室37和第二环形气缸11b导通，在第一密封件22上还设置有将扇形槽222外周密封的密封环40，密封环40上设有一个径向的通孔401，通孔401与贮气燃烧室37连通。可以由旋转的第一密封件22来将喷气通道38导通或关闭，当喷气通道38的入口与贮气燃烧室37的出口相对时，喷气通道38导通。密封环可以是单独的零件，也可以设置成与气缸体为整体结构。
如图27、图28所示，本实施例中的喷气口设置有三个，一个主喷气口41和两个副喷气口42，副喷气口42在第一密封件22的旋转方向上位于主喷气口41的后侧，副喷气口42上设置有喷气口单向阀43，只有当贮气燃烧室37中的压力超过喷气口单向阀43的弹簧力后，才能推开阀门使燃气进入第二环形气缸11b，若是副喷气口42未旋转进入膨胀室C，贮气燃烧室37中的燃气压力将不足以推开喷气口单向阀43而通过副喷气口42泄气，为了多进气而给予多个气体进入膨胀室C的通道，实现快速膨胀做功，设置多个喷气口。
第一环形气缸11a的进气口12和第二环形气缸11b的出气口14分别与进气管和排气管相连，由第一环形气缸11a完成吸气压缩，第二环形气缸11b完成作功排气。如图18和图19所示，所述传动轴21的轴端设置有作为驱动轮的链轮，驱动轮通过传动机构48带动转轴17旋转，传动机构48包括链轮链条副和锥齿轮副，同侧的一对第二密封件16的旋转方向相同。
本技术方案的结构和工作原理与实施例1基本相同，只是为两个并列的环形气缸11，吸气和压缩由第一环形气缸11a完成，而膨胀和做功用第二环形气缸11b完成，两个气缸并列设置并分工，其相较于前述第一个技术方案而言，其更优的效果在于：1、能降低成本和增加性能的稳定性；2、气体从压缩室B进入膨胀室C容易从技术上实现，这样既能降低技术难度又能降低制造和维修成本，更能简化结构和增大工作的稳定性；3、第一技术方案中，燃烧室 处的第二密封件16与活塞23必须要两侧都具有很好的密封性，在选材和制作工艺上要求较高，而本技术方案中，当活塞23穿过第二密封件16时，第二密封件16和活塞23两侧的密封程度只需要保证一侧具有稳定和良好的密封性即可(压缩气体的一侧或者气体膨胀的一侧)，这样从现有的材质和技术上都能容易实现；4、在活塞23旋转一周的情况下，气体的做功行程是第一技术方案的两倍，燃烧和做功完全，这样能提高效率和降低燃油的成本。
实施例4：
如图29、图30所示本实施例与实施例3基本相同，所不同的是，所述喷气通道38设置在第二环形气缸11b的第二气缸体1b上，喷气通道38与第二环形气缸11b连通，在所述贮气燃烧室37的出口位置设置有可开闭的喷气阀45，在压缩冲程末期至膨胀作功冲程结束时，所述喷气阀45打开。如图所示，喷气阀45为一个旋转阀，其阀片为半圆形，当压缩冲程时阀片的半圆形部分将贮气燃烧室37的出口遮挡，而压缩冲程结束即将进行点火直至膨胀作功冲程结束，其阀片打开，贮气燃烧室37内的气体可以通过第二气缸体1b上的喷气通道38进入膨胀室C。
实施例5：
如图31至图38所示，本实施例与实施例3基本相同，所不同的是，采用双活塞，以获得更佳的动平衡，工作机运行更加平稳。与之相适应地，贮气燃烧室37、喷气通道、喷气口、活塞23和第二密封件16为两套。每个气缸体1上设置有呈180度对称的两个挡块安装口15，两个挡块安装口15为长条形并且平行设置，两第二密封件16为一端大一端小的圆盘形，第二密封件16的大端端面16a均位于通过传动轴21轴线的平面上；所述第一密封件22上设置有呈180度对称的两个活塞23，两个活塞23和两个第二密封件16将所述环形气缸11分隔为四个腔室，第一环形气缸11a的两个挡块安装口15之间设置有进气口12和出气口14，即第一环形气缸11a上设置有两个进气口12和两个出气口14，进气口12和出气口14间隔布置，第一环形气缸11a的出气口14，通过贮气燃烧室37和喷气通道38与第二环形气缸11b的进气口连接,第二环形气缸11b上与之相对应地设置有两个分别与排气管相连通的出气口14。为了降低环形气缸的温度，如图34、图37和图38所示在第一密封件22内设置了与传动轴21内的冷却孔相接通的冷却液通道223，并且冷却液通道223将第一密封件22的外圆周贯通，在两个环形气缸体内也设置了冷却液通道1c(仅图示了第一气缸体1a)。贮气燃烧室37、喷气通道、喷气口、活塞23和扇形槽222的结构与实施例3相同，喷气通道也可采用实施例4的结构。如图31和图34所示，实施例3中的密封环40与第一气缸体1a为整体结构，在第一气缸体1a上开设有与贮气燃烧室连通的通孔401，第一密封件22的外圆周上 设有周向的环槽，环槽中安装有环形的密封条，第一密封件22与两气缸体相接触的部位之间设有环形的密封条；活塞23与两气缸体相接触的部位之间设有密封条或者密封片，传动轴21上设置有主动锥齿轮49，主动锥齿轮49与从动锥齿轮50啮合，然后通过传动机构48带动4根转轴17旋转，传动机构48包括多个相啮合的齿轮。
实施例6：
如图39至图41所示，本实施例与实施例5基本相同，所不同的是，连通两环形气缸的通道不是贮气燃烧室和喷气通道，而只是将第一环形气缸11a和第二环形气缸11b的出气口14用一根三通管46相连通再与排气管47相接，就可作为空压机使用。每个挡块安装口15两侧的气缸壁上分别设有进气口12和出气口14，进、出气口12、14沿气缸周向交替分布，所述出气口14与排气管连通。同侧的两个第二密封件16的旋转方向相反。动力经传动轴21接入驱动活塞23运动，压缩气体，每个环形气缸可以设置两个活塞23和两个挡块安装口15，气体经压缩后从出气口14排出经排气管进入外部储气罐，由于两个气缸体内腔较大，活塞23旋转一圈能够压缩更多气体，使压缩效率提高。图39示出了单活塞结构时的空压机。
利用本工作机的原理还可以改装成抽气机或者液体的抽压机。

Claims (11)

  1. 一种旋转活塞式工作机，其特征在于：包括环状或盘状的气缸体，所述气缸体上沿气缸体的周向开设有一圈环形槽，所述气缸体轴线上设置有传动轴，该传动轴上连接有第一密封件，所述第一密封件将所述环形槽密封，并与所述气缸体围成密闭的环形气缸，在环形气缸内的所述第一密封件上设置有至少一个活塞，所述活塞与环形气缸适配；
    所述气缸体上沿周向开设有至少一个挡块安装口，在气缸体外部由转轴支撑的第二密封件伸入所述挡块安装口，第二密封件与所述活塞将所述环形气缸分隔为至少两个腔室，所述第二密封件上开设有至少一个活塞过孔，所述活塞绕传动轴旋转，并沿环形气缸做周向运动，所述第二密封件绕转轴旋转，在所述活塞转动至第二密封件时，所述第二密封件转动至活塞过孔与活塞对应的位置，使活塞刚好通过所述活塞过孔，且所述第二密封件在运动过程中将所述挡块安装口以及挡块安装口两边的腔室密封，所述气缸体上设有进气口和出气口。
  2. 根据权利要求1所述的旋转活塞式工作机，其特征在于：所述活塞为两个，两个活塞相对于所述传动轴对称设置，所述挡块安装口为两个，两个活塞和两个第二密封件将所述环形气缸分隔为四个腔室；所述进气口和出气口分别设置在其中一个第二密封件两侧的气缸壁上，另一个第二密封件两侧的气缸壁上分别开设有贮气口和喷气口，该贮气口和喷气口设置有密封阀，贮气口和喷气口之间设有贮气燃烧室；或所述活塞上设置有导气孔，导气孔沿活塞长度方向延伸并且该导气孔两端设置有单向阀，两个单向阀之间围成贮气燃烧室；所述传动轴的轴端设置有驱动轮，驱动轮通过传动机构带动转轴旋转。
  3. 根据权利要求2所述的旋转活塞式工作机，其特征在于：所述气缸体和第一密封件呈盘状并且同轴并列对置，所述传动轴通过轴承与气缸体连接，在所述第一密封件和气缸体的对置端面上分别设置所述活塞和环形槽，第一密封件和气缸体的对置端面贴合而形成所述环形气缸。
  4. 根据权利要求3所述的旋转活塞式工作机，其特征在于：所述转轴和传动轴的轴线垂直交错，所述第一密封件位于环形气缸的部分内凹，所述第二密封件为圆盘状，该第二密封件外圆周与所述第一密封件相接触，第二密封件对称开有两个活塞过孔，两个所述第二密封件由传动机构带动而相反向地旋转。
  5. 根据权利要求2或3或4所述的旋转活塞式工作机，其特征在于：所述第二密封件的活塞过孔的形状与所述活塞的形状对应，所述活塞的前、后侧面为倾斜延伸的螺旋形曲面，活塞的左、右侧面与环形气缸的侧壁贴合，在活塞运动方向的投影上，所述活塞的形状呈扇形，所述活塞过孔为扇形孔，在活塞和第二密封件相遇的过程中，所述活塞过孔的内壁与活塞外轮廓面保持贴合。
  6. 一种旋转活塞式工作机，其特征在于：包括同轴并列的两个盘状的气缸体，两气缸体上分别开设有一圈环形槽，两气缸体的环形槽开口相向，两所述气缸体之间夹装有第一密封件，两环形槽与第一密封件的两侧贴合而分别形成密闭的两个环形气缸，传动轴通过轴承安装在气缸体轴线上并且与第一密封件固定连接；在环形气缸内的所述第一密封件上设置有至少一个活塞，所述活塞与环形气缸适配；
    所述气缸体上至少开设有一个横向连通环形气缸的挡块安装口，两气缸体同侧的挡块安装口相邻而组成一对挡块安装口，在气缸体外部由转轴支撑的第二密封件伸入所述挡块安装口，第二密封件与所述活塞将每个所述环形气缸分隔为至少两个腔室，所述第二密封件上开设有至少一个活塞过孔，所述活塞绕传动轴旋转，并沿环形气缸做周向运动，所述第二密封件绕转轴旋转，在所述活塞转动至第二密封件时，所述第二密封件转动至活塞过孔与活塞对应的位置，使活塞刚好通过所述活塞过孔，且所述第二密封件在运动过程中将所述挡块安装口以及挡块安装口两边的腔室密封；每个挡块安装口两侧的环形气缸上分别设置有进气口和出气口，在每对挡块安装口旁侧设置有将两环形气缸连通的通道。
  7. 根据权利要求6所述的旋转活塞式工作机，其特征在于：所述通道包括贮气燃烧室和相连接的喷气通道，贮气燃烧室中设置有火花塞或喷油嘴，第一环形气缸的出气口通过单向阀与贮气燃烧室相接，喷气通道的喷气口为第二环形气缸的进气口，第一环形气缸的进气口和第二环形气缸的出气口分别与进气管和排气管相连，第一环形气缸完成吸气压缩，第二环形气缸完成作功排气，所述传动轴的轴端设置有驱动轮，驱动轮通过传动机构带动转轴旋转。
  8. 根据权利要求7所述的旋转活塞式工作机，其特征在于：所述喷气通道设置在第一密封件上，在压缩冲程末期至膨胀作功冲程结束时，第一密封件上喷气通道将贮气燃烧室和第二环形气缸导通；或者是所述喷气通道设置在第二环形气缸的第二气缸体上，在所述喷气通道的出口位置设置有可开闭的喷气阀，在压缩冲程末期至膨胀作功冲程结束时，所述喷气阀打开。
  9. 根据权利要求7所述的旋转活塞式工作机，其特征在于：所述喷气通道包括设置在第一密封件上的扇形槽，扇形槽的槽口开设在第一密封件外圆表面的中部，在与第二环形气缸相对应的第一密封件表面上开设有连通扇形槽的喷气口，在压缩冲程末期至膨胀作功冲程结束时，第一密封件的喷气通道将贮气燃烧室和第二环形气缸导通，在第一密封件上还设置有将扇形槽外周密封的密封环，密封环上设有径向的通孔，通孔与贮气燃烧室连通。
  10. 根据权利要求6或8所述的旋转活塞式工作机，其特征在于：第一密封件的端面上设置有与所述环形槽相对应的第二环形槽，第二环形槽的槽底为圆弧形，所述第二密封件为 一端大一端小的圆盘形；所述气缸体上设置有呈180度对称的两个平行的挡块安装口，第二密封件的大端端面均位于通过传动轴轴线的平面上，所述第一密封件上设置有呈180度对称的两个活塞，两个活塞和两个第二密封件将所述环形气缸分隔为四个腔室；第一环形气缸的的两个挡块安装口之间设置有进气口和出气口，所述喷气通道为两个。
  11. 根据权利要求1或6所述的旋转活塞式工作机，其特征在于：每个所述挡块安装口两侧的气缸壁上分别设有进气口和出气口，进、出气口沿环形气缸周向交替分布，所述出气口与排气管连通。
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