Crank connecting rod movement device, power equipment and piston engine operation method

Abstract

The invention relates to a crank connecting rod movement device, power equipment and a piston type engine operation method.The crank connecting rod movement device comprises a crank, a connecting rod and a linear sliding piece and further comprises a driven sliding block, a sliding actuator, a clutch mechanism and a position keeping mechanism, the sliding actuator and the linear sliding piece are connected and move synchronously, and the driven sliding block is hinged to the connecting rod; the clutch mechanism is arranged between the driven sliding block and the sliding actuator and has a transmission connection state and a transmission disconnection state. When the driven sliding block reaches the upper limit position, the crank is located at a zero phase angle, and a transmission disconnection angle and a transmission connection angle are arranged in front of and behind the zero phase angle respectively; the clutch mechanism is in a transmission connection state in the process that the crank rotates from the transmission connection angle to the transmission disconnection angle, and the clutch mechanism is in a transmission disconnection state in the process that the crank rotates from the transmission disconnection angle to the transmission connection angle; the position maintaining mechanism locks the position of the linear sliding piece when the crank reaches a transmission disconnection angle, and the position maintaining mechanism unlocks the position when the crank reaches a transmission connection angle.

Description

Technical Field

[0001] The present invention relates to the technical field of engines, and particularly to a crank - connecting rod motion device, a power equipment, and a piston - type engine operation method. Background Art

[0002] The basic moving components of existing piston engines are crank - connecting rod mechanisms, in which the piston (including the piston rod), the connecting rod, and the crankshaft respectively correspond to the slider, the connecting rod, and the crank in the crank - connecting rod mechanism. In order to make the combustion more complete and increase the peak pressure of the gas, without changing the initial conditions such as the geometric dimensions of the engine and the fuel, existing spark - ignition engines generally adopt the method of advanced ignition, that is, ignition before the piston reaches the top dead center. There are at least the following four major disadvantages in the arrangement of the structure and ignition timing of such engines: (1) Ignition before the top dead center means that part of the fuel in the air - fuel mixture starts to burn and generate gas before the end of the compression stroke. At the same time, as the piston continues to move towards the top dead center, it has to compress the gas with an expanding tendency, which will increase the useless work and reduce the efficiency of the engine; (2) Due to the structural principle, the peak value of the cylinder pressure always appears when the crank angle is very small. At this time, on the force - transmission path, when the driving force acting on the piston is transmitted to the crank, the force arm relative to the crank rotation center is very small, and the driving torque that can be generated is limited, resulting in that although the pressure of the gas is very high, it cannot generate a large enough torque on the crank accordingly; (3) The principle of the traditional crank - connecting rod mechanism determines that within a relatively large angle range after the crank passes through the dead center, the movement speed of the piston is relatively low, which limits the speed of gas expansion work. After the crank passes through a certain angle (which can be called the starting angle of the preferred transmission range) after the top dead center and reaches the preferred transmission range, the pressure in the cylinder has seriously decayed, and more than half of the expansion potential energy of the gas has been consumed. Therefore, even if a very high peak pressure is obtained near the top dead center, the best work - doing ability of the gas cannot be effectively utilized, which greatly restricts the power of the engine; (4) Theoretically, except at the moment of reaching the top and bottom dead centers, the piston is always in motion. After the piston passes through the top dead center, the space where the fuel is located gradually increases with the movement of the piston. Therefore, unless the combustion is just completed when the piston reaches the top dead center, the actual combustion space is larger than the combustion chamber space, that is, the space where the air - fuel mixture burns is larger than the space it occupies after being compressed to the maximum extent. In this way, under the conditions of the mixture ratio, compression ratio, and equal fuel injection volume, the peak pressure and temperature obtained by existing internal combustion engines will be lower than the values that can be achieved when the oil - gas mixture is completely confined in the combustion chamber space for combustion. Changing this state and avoiding combustion in an increasing space is an important way to improve fuel efficiency.

[0003] Therefore, in the case of a traditional piston internal combustion engine, the moment when the peak pressure appears is far from the moment when the crank reaches the preferred transmission range. The structural principle determines that the two are contradictory and cannot be unified. On the one hand, in order to obtain a higher peak pressure, the mixed gas needs to burn in the space compressed to the minimum volume. The pressure in the cylinder can reach the peak within milliseconds, approaching or exceeding 10 MPa, and the temperature approaches or exceeds 2000 K. However, when obtaining such high-energy gas, the crank angle is approximately 20 degrees after top dead center and has not reached the upper limit point of the preferred transmission range (generally taken as 40 degrees after top dead center). On the other hand, if the ignition is postponed to take care of the crank entering the upper limit point of the preferred transmission range, the peak pressure will be greatly reduced, and the torque and efficiency of the engine cannot be significantly improved. In short, the structure of the traditional internal combustion engine limits its efficiency and power. Summary of the Invention

[0004] In view of the above-mentioned disadvantages of the prior art, the technical problem to be solved by the present invention is to provide a crank connecting rod motion device, a power device, and a piston engine operation method. When the crank is in the region near the zero-degree phase angle, the linear sliding member can stay stationary at the upper limit position for a period of time, which can overcome the inherent weakness that the peak pressure of the piston internal combustion engine necessarily appears near the dead center, without the need for early ignition, can obtain a higher peak pressure, and has a greater output torque and higher fuel efficiency.

[0005] To achieve the above object, the present invention provides a crank - connecting rod motion device, which includes a crank, a connecting rod, and a linear slider. One end of the connecting rod is hinged to the crank. The linear slider moves linearly in the up - and - down direction and is located above the crank. The device further includes a passive slider, a sliding actuator, a clutch mechanism, and a position - holding mechanism. The sliding actuator is connected to the linear slider and the two move linearly synchronously. The passive slider is hinged to the other end of the connecting rod. The clutch mechanism is arranged between the passive slider and the sliding actuator, and the clutch mechanism has a transmission - connected state and a transmission - disconnected state. When the clutch mechanism is in the transmission - connected state, the passive slider establishes a motion connection with the sliding actuator and moves up and down synchronously. When the clutch mechanism is in the transmission - disconnected state, the passive slider disconnects the motion connection with the sliding actuator, and the passive slider can move linearly up and down relative to the linear slider. When the passive slider reaches the upper limit position, the phase angle corresponding to the crank is the zero - phase angle, and a transmission - disconnected angle and a transmission - connected angle are respectively provided before and after the zero - phase angle along the rotation direction. When the crank rotates from the transmission - disconnected angle to the transmission - connected angle, the passive slider first moves upward to the upper limit position and then moves downward away from the upper limit position. During the process of the crank rotating from the transmission - connected angle to the transmission - disconnected angle, the clutch mechanism is in the transmission - connected state. During the process of the crank rotating from the transmission - disconnected angle to the transmission - connected angle, the clutch mechanism is in the transmission - disconnected state, and the linear slider is located at its upper limit position. When the crank is at the transmission - connected angle and the transmission - disconnected angle, the clutch mechanism completes the state switch. When the crank reaches the transmission - disconnected angle, the position - holding mechanism is triggered to act and can lock the position of the linear slider. When the crank reaches the transmission - connected angle, the position - holding mechanism is triggered to act and releases the position lock of the linear slider.

[0006] Further, a driving boss is fixedly provided on the passive slider. The sliding actuator includes a driving block, a driving bolt, and a first return spring. The driving block linearly moves in the up and down direction and is directly or indirectly connected to the linear sliding member. One end of the driving bolt is hinged to the driving block, and the other end is a swinging end. The driving bolt is located above the driving boss. The first return spring is installed on the driving block and acts on the driving bolt. The first return spring applies an elastic force to the driving bolt to drive the driving bolt to swing downward until the swinging end presses against the driving boss. The clutch mechanism includes a top block, a locking block, a second return spring, a third return spring, an action execution component, and a triggering component. The top block, the locking block, the second return spring, the third return spring, and the action execution component are all installed on the passive slider. The top block is located above the driving boss and on one side of the swinging end of the driving bolt. The top block can linearly move relative to the passive slider to approach or move away from the swinging end of the driving bolt. The second return spring acts on the top block and provides an elastic force to drive the top block to press against the swinging end of the driving bolt. The locking block can linearly move up and down relative to the passive slider, and when the locking block moves, it can enter or leave the side of the top block away from the driving bolt through a guiding surface. The third return spring acts on the locking block and provides an elastic force to drive the locking block to enter the side of the top block away from the driving bolt and abut against it. The action execution mechanism is connected to the locking block. The triggering component cannot translate in the left and right directions. During the process of the crank rotating from the transmission connection angle to the transmission disconnection angle, the locking block abuts against the top block, and the swinging ends of the driving bolts respectively abut against both the top block and the driving boss. When the crank rotates to the transmission disconnection angle, the action execution component contacts and acts on the triggering component and drives the locking block away from the top block. When the crank rotates to the transmission connection angle, the action execution component disengages from the triggering component, and the locking block resets to the side of the top block away from the driving bolt and abuts against it.

[0007] Further, the action execution mechanism includes an action execution swing arm and an action execution connecting rod. The middle of the action execution swing arm is hinged to the passive slider, and one end thereof is a triggering action end, and the other end is hinged to one end of the action execution connecting rod. The other end of the action execution connecting rod is hinged to the locking block. The triggering component includes an action claw and a fixed limiting rod located above the action claw. The fixed limiting rod extends in the up and down direction. A triggering inclined surface is provided on the action claw. When the passive slider moves from the lower limit position to the upper limit position, the triggering action end of the action execution swing arm can contact the triggering inclined surface and then abut against the fixed limiting rod. When the triggering action end of the action execution swing arm moves along the triggering inclined surface, the action execution swing arm rotates and drives the locking block away from the top block through the action execution connecting rod, and the locking block remains in the separated state when the triggering action end abuts against the fixed limiting rod.

[0008] Further, the action claw is rotatably mounted, and an upwardly facing slack surface is provided on the action claw. The trigger assembly further includes a fourth return spring, which acts on the action claw and provides an elastic force to urge the action claw to abut against the lower end of the fixed limit rod. When the passive slider moves from the upper limit position to the lower limit position, the trigger action end of the action execution swing arm abuts against the slack surface of the action claw, forcing the action claw to rotate downward and swing, and the execution swing arm can smoothly rotate until the lock block enters the side of a top block away from the drive bolt.

[0009] Further, a downwardly facing locking inclined surface and a transition surface connected to the upper side edge of the locking inclined surface are provided on the drive block of the sliding actuator. The position holding mechanism includes a fixed support, a latch, a latch block, a lever, a push arm, a fifth return spring, a sixth return spring, a holding support plate, a wedge block assembly, and an extended trigger structure. The latch is rotatably mounted on the fixed support and is provided with a top holding portion and a rotation blocking portion. The fifth return spring is disposed between the fixed support and the latch and applies an elastic force to urge the latch to rotate until the top holding portion is located at the position of the locking inclined surface of the drive block when in the upper limit position. The latch block is mounted on the fixed support and can move linearly up and down. The lever is fixed to the latch block. The sixth return spring is disposed on the fixed support and applies an elastic force to the latch block to urge it to move leftward until it abuts against the rotation blocking portion of the latch and prevents the latch from rotating. The middle of the push arm is hinged to the fixed support, and its first end is located below the lever and the second end is for contacting the wedge block. The wedge block assembly is mounted on the passive slider and includes a wedge block and a telescopic drive portion for driving the wedge block to be in an extended or retracted state. The holding support plate is connected to the drive block and is located above the transition surface. When the linear slider is in its upper limit position, the top holding portion of the latch presses on the locking inclined surface, and when the passive slider is also in its upper limit position, the wedge block is located above the second end of the push arm. When the passive slider moves downward from the upper limit position, the extended wedge block will push the second end of the push arm to rotate, and when the push arm rotates, the first end will push the lever to move the latch block to move away from the rotation restriction of the latch. When the holding support plate moves downward with the passive slider, it can abut against both the top holding portion and the second end of the push arm, preventing the latch from resetting and rotating and the latch block from resetting and moving downward. When the linear slider is in its upper limit position and the passive slider moves upward to reach its upper limit position, the extended trigger structure triggers the telescopic drive portion to move downward relative to the passive slider to the in-place position so that the wedge block is in the extended state.

[0010] Further, the position holding mechanism further includes a retraction trigger structure. When the wedge block moves downward with the passive slider until it is located below the push arm and the passive slider reaches its lower limit position, the retraction trigger structure triggers the telescopic drive portion to move upward relative to the passive slider to the in-place position so that the wedge block is in the retracted state.

[0011] Further, the telescopic driving part of the wedge block assembly includes a bracket, a guide frame, an action slider, a passive action part, and a switching transmission structure. The bracket is fixed on the passive slider, the guide frame is fixed to the bracket, the wedge block is installed in the guide frame and can move linearly outwards or retract, the action slider is installed on the bracket and can move linearly up and down in the bracket. An extending connection structure and a retracting connection structure located below the extending connection structure are provided on the action slider. The passive action part is installed on the bracket and is used for kinematically connecting with the extending connection structure or the retracting connection structure. The switching transmission structure connects the passive action part and the wedge block. When the action slider moves downward relative to the bracket, the passive action part moves to the position of the extending connection structure, and the switching transmission structure drives the wedge block to change to the extended state. When the action slider moves upward relative to the bracket, the passive action part moves to the position of the retracting connection structure, and the wedge block changes to the retracted state; the extending trigger structure and the retracting trigger structure respectively include an extending upper boss and a retracting lower boss; when the linear sliding part is at the upper limit position, the upper end of the action slider abuts against the extending upper boss, and when the wedge block assembly moves downward with the passive slider, the lower end of the action slider will abut against the retracting lower boss.

[0012] Further, the extending connection structure and the retracting connection structure on the action slider respectively include a first cylindrical concave surface and a second cylindrical concave surface, and the first cylindrical concave surface and the second cylindrical concave surface are connected by an inclined surface. The passive action part is an action wheel, and the action wheel can be placed in the first cylindrical concave surface and the second cylindrical concave surface and can move between the two. The switching transmission structure includes a first switching swing arm, a second switching swing arm, a switching connecting rod, and a lifting wheel. The middle parts of the first switching swing arm and the second switching swing arm are rotatably installed on the bracket. One end of the first switching swing arm is connected to the action wheel, and the other end is hinged to one end of the switching connecting rod. The other end of the switching connecting rod is hinged to one end of the second switching swing arm. The other end of the second switching swing arm is connected to the lifting wheel, and the lifting wheel abuts against one end of the wedge block. When the action wheel moves from the second cylindrical concave surface to the first cylindrical concave surface, the lifting wheel jacks up the wedge block to the extended state; the wedge block assembly further includes a seventh return spring installed on the bracket, and the seventh return spring acts on the wedge block to provide an elastic force to drive the wedge block to reset to the retracted state.

[0013] Further, the position holding mechanism includes a guide wheel group, and the guide wheel group includes a plurality of guide wheels arranged linearly in the up and down direction. The inner side of the driving block abuts against the passive slider, and the outer side can abut against the guide wheel group when the driving block moves downward.

[0014] Further, the driving block and the linear sliding member are connected by a flexible connection assembly. The flexible connection assembly includes a connection block and a transfer block. The connection block is rotatably connected to the linear sliding member, and the rotation axis is perpendicular to the rotation plane of the crank. The upper end of the transfer block is pivotally connected to the connection block, and the lower end is pivotally connected to the driving block. The rotation axis between the transfer block and the connection block is perpendicular to the moving direction of the linear sliding member and perpendicular to the rotation axis between the connection block and the linear sliding member. The rotation axis between the transfer block and the driving block is parallel to the rotation axis between the connection block and the linear sliding member.

[0015] The present invention also provides a power device, including a cylinder piston device. The cylinder piston device includes a cylinder, a piston located in the cylinder, and a piston rod connected to the piston. The power device further includes the above-mentioned crank connecting rod motion device, and the linear sliding member of the crank connecting rod motion device is fixedly connected to the piston rod or is integral with the piston rod.

[0016] Further, an inner core hole and N-stage sleeve inner holes are sequentially arranged in the cylinder from top to bottom, where N≥1, and the cross-sections increase sequentially from the inner core hole to the N-stage sleeve inner holes. There are inter-stage stepped surfaces between the inner core hole and the uppermost first-stage sleeve inner hole, and between adjacent two-stage sleeve inner holes. The piston sequentially includes a piston core and N-stage piston sleeves from inside to outside. The innermost first-stage piston sleeve is sleeved on the piston core and can move relatively up and down. When N≥2, the outer-stage piston sleeve is sleeved on the inner-stage piston sleeve and can move relatively up and down. Inner piston rings are provided between the piston core and the first-stage piston sleeve, and between adjacent two-stage piston sleeves. The lower end of the piston core is connected to a piston rod. A first limit stop surface and a second limit stop surface are respectively provided on the piston core and the first-stage piston sleeve, and the piston core can move upward relative to the first-stage piston sleeve until the first limit stop surface abuts against the second limit stop surface. Third limit stop surfaces and fourth limit stop surfaces are respectively provided on adjacent two-stage piston sleeves, and the inner-stage piston sleeve can move upward relative to the outer-stage piston sleeve until the third limit stop surface abuts against the fourth limit stop surface. The N-stage piston sleeve is located in the N-stage sleeve inner hole. When the piston core is at its top dead center, the upper end of the piston core is located in the inner core hole, the upper ends of the i-stage piston sleeves are respectively located in the i-stage sleeve inner holes, where N≥i≥1, and the first limit stop surface and the second limit stop surface of the piston core and the first-stage piston sleeve abut against each other, and the third limit stop surface and the fourth limit stop surface of adjacent two-stage piston sleeves abut against each other. The cylinder piston device further includes a sleeve locking mechanism, a force transmission mechanism, and a force transmission release mechanism. Force transmission mechanisms are respectively provided on the piston core and the piston sleeves within the Nth stage. The force transmission mechanism includes a force transmission pin disposed in a force transmission pin hole on the outer side surface of the piston core or the piston sleeve, and a force transmission elastic structure acting on the force transmission pin. The force transmission pin can move in the force transmission pin hole to extend or retract into the force transmission pin hole. The force transmission elastic structure applies an elastic force to the force transmission pin to drive the force transmission pin to move outward. When the first limit stop surface of the piston core abuts against the second limit stop surface on the first-stage piston sleeve, the force transmission pin on the piston core is located above the lower end surface of the piston sleeve. When the third limit stop surface and the fourth limit stop surface of adjacent two-stage piston sleeves abut against each other, the force transmission pin on the inner piston sleeve is located above the lower end surface of the outer piston sleeve. When the piston core reaches the top dead center, the positions of all piston sleeves can be locked by the sleeve locking mechanism. When the piston core descends from its top dead center until the upper end of the force transmission pin on it reaches the lower end surface of the first-stage piston sleeve, the force transmission pin extends out of the force transmission pin hole and the sleeve locking mechanism releases the locking of the piston sleeve. When the inner piston sleeve among adjacent two-stage piston sleeves descends from its top dead center until the upper end of the force transmission pin on it reaches the lower end surface of the outer piston sleeve, the force transmission pin extends out of the force transmission pin hole and the sleeve locking mechanism releases the locking of the outer piston sleeve. When the piston core descends to its bottom dead center, the force transmission release mechanism contacts the force transmission pin in the extended state and compresses the force transmission pin into the force transmission pin hole.

[0017] Further, the cylinder is provided with an unlocking pin through hole, a retaining pin through hole, and a locking pin through hole, and the retaining pin through hole is located below the locking pin through hole. The sleeve locking mechanism includes a force transmission plate, a locking elastic structure, an unlocking pin, a retaining pin, and a locking pin. The unlocking pin, the retaining pin, and the locking pin are respectively located in the unlocking pin through hole, the retaining pin through hole, and the locking pin through hole. The outer ends of the unlocking pin, the retaining pin, and the locking pin are all connected to the force transmission plate and move with the force transmission plate. The locking elastic structure applies an elastic force to the force transmission plate to drive the force transmission plate to press against the outer wall of the cylinder. At this time, the inner ends of the unlocking pin, the retaining pin, and the locking pin all extend into the cylinder. When the force transmission plate approaches or moves away from the cylinder, the unlocking pin, the retaining pin, and the locking pin can synchronously extend or retract into the inner wall of the cylinder. The sleeve locking mechanism is N in number and is used to lock N-stage piston sleeves respectively. When the piston sleeve is at the top dead center, the locking pin of the corresponding sleeve locking mechanism abuts against the lower end face of the piston sleeve. An unlocking block is fixedly provided on the piston core, and when N≥2, unlocking blocks are also fixedly provided on the piston sleeves within the Nth stage. An unlocking inclined surface is provided on the lower side of the unlocking block. When the piston core descends from its top dead center, the unlocking inclined surface of the unlocking block on it can contact the unlocking pin of the sleeve locking mechanism used to lock the ith-stage piston sleeve and drive the unlocking pin to move outward until it retracts into the inner wall of the cylinder. When N≥2, when the inner piston sleeve of two adjacent stages of piston sleeves descends from its top dead center, the unlocking inclined surface of the unlocking block on it can contact the unlocking pin of the sleeve locking mechanism used to lock the outer piston sleeve and drive the unlocking pin to move outward until it retracts into the inner wall of the cylinder. When the piston sleeve leaves its top dead center, at least one of the unlocking pin, the retaining pin, and the locking pin of the corresponding sleeve locking mechanism abuts against the outer peripheral surface of the piston sleeve.

[0018] The present invention also provides a piston engine operation method. The piston engine includes the above-mentioned power device, and also includes an intake valve, an exhaust valve, and an ignition device. When the passive slider in the power device is at its lower limit position, the corresponding angle of the crank is the bottom dead center angle. The piston engine operation method includes the following processes:

[0019] A1. Exhaust stroke process: The exhaust valve opens, the crank rotates from the bottom dead center angle towards the transmission disconnection angle, the clutch mechanism maintains the transmission connection state, the piston rod ascends from its lower dead center, the piston discharges the waste gas in the cylinder, and when the crank reaches the transmission disconnection angle, the piston rod reaches its top dead center, and the position maintaining mechanism locks the position of the piston rod, and the clutch mechanism switches to the transmission disconnection state;

[0020] A2. Intake waiting process: The clutch mechanism maintains the transmission disconnection state, the crank rotates from the transmission disconnection angle to the zero phase angle and then to the transmission connection angle, the piston rod remains at its top dead center, and when the crank reaches the transmission connection angle, it switches to the transmission connection state, the exhaust valve closes, and the intake valve opens;

[0021] A3. Intake stroke process: The crank rotates from the transmission connection angle to the bottom dead center angle, the clutch mechanism maintains the transmission connection state, the piston moves downward, and when the crank reaches the bottom dead center angle, the piston rod reaches its lower dead point and the intake valve closes.

[0022] A4. Compression stroke process: The crank rotates from the bottom dead center angle towards the transmission disconnection angle, the clutch mechanism maintains the transmission connection state, the piston rod moves upward, and the piston compresses the gas in the cylinder. When the crank reaches the transmission disconnection angle, the piston rod reaches its upper dead point, and the position holding mechanism locks the position of the piston rod, and the clutch mechanism switches to the transmission disconnection state.

[0023] A5. Waiting for ignition and combustion delay process: The crank rotates from the transmission disconnection angle to the zero phase angle and then to the transmission connection angle, the piston rod remains at its upper dead point, ignition is carried out at any time point during this period, and the clutch mechanism switches to the transmission connection state when the crank reaches the transmission connection angle.

[0024] A6. Power stroke process: The clutch mechanism maintains the transmission connection state, the high-pressure gas in the cylinder drives the piston to move downward, and the piston rod drives the crank to rotate from the transmission connection angle to the bottom dead center angle, and the piston rod reaches its lower dead point.

[0025] As described above, the crank connecting rod motion device, power equipment, and piston engine operation method involved in the present invention have the following beneficial effects:

[0026] Compared with the direct connection method between the connecting rod and the slider in the existing traditional crank connecting rod mechanism, in the crank connecting rod motion device of the present invention, by setting a passive slider, a sliding actuator, and a clutch mechanism between the connecting rod and the linear slider for connection, it can automatically disconnect or connect between the connecting rod and the linear slider according to the crank position. During the continuous rotation of the crank, in the area near the zero phase angle, the linear slider can stay stationary at the upper limit position for a period of time, which can overcome the weakness that the peak pressure inherent in the piston internal combustion engine necessarily appears near the dead point, without the need for early ignition, and can obtain a higher peak pressure, with a larger output torque and higher fuel efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 It is a schematic structural diagram of the crank connecting rod device of the present invention.

[0028] Figure 2 It is a schematic structural diagram of the passive slider and the sliding actuator in the present invention.

[0029] Figure 3 It is a schematic structural diagram of the passive slider and the sliding actuator in the present invention.

[0030] Figure 4 It is a schematic connection diagram of the clutch mechanism with the passive slider and the sliding actuator in the present invention.

[0031] Figure 5 Schematic diagram of the working state when the clutch mechanism in the present invention is in the transmission-disconnected state.

[0032] Figure 6 Schematic diagram of the working state when the clutch mechanism in the present invention is in the transmission-connected state.

[0033] Figure 7 Schematic diagram when the position-holding mechanism in the present invention locks the driving block.

[0034] Figure 8 Schematic diagram of the structure of the position-holding mechanism in the present invention.

[0035] Figure 9 Schematic diagram when the wedge block of the wedge block assembly in the present invention is in the retracted state.

[0036] Figure 10 Schematic diagram when the wedge block of the wedge block assembly in the present invention is in the extended state.

[0037] Figure 11 Exploded view of the wedge block assembly in the present invention.

[0038] Figure 12 Schematic diagram of the structure of the piston engine in the present invention.

[0039] Figure 13 Schematic diagram of the structure outside the cylinder piston device in the present invention.

[0040] Figure 14 Half-sectional view of the cylinder piston device in the present invention.

[0041] Figure 15 Schematic diagram of the installation of the force transmission pin and the unlocking block in the piston in the present invention.

[0042] Figure 16 Schematic diagram when both the piston core and the piston sleeve of the piston in the present invention are at the top dead center.

[0043] Figure 17 Schematic diagram of the working state when the unlocking pin and the holding pin both abut against the piston sleeve when the piston in the present invention is moving downward.

[0044] Figure 18 Schematic diagram of the working state when the piston core approaches its bottom dead center in the present invention.

[0045] Figure 19 Schematic diagram of the working state when the force transmission pin enters the piston sleeve when the piston core moves upward from the bottom dead center in the present invention.

[0046] Figure 20 Schematic diagram of the structure of the cylinder in the present invention.

[0047] Figure 21 Half-sectional view of the cylinder in the present invention.

[0048] Figure 22 Schematic structural view of the piston core in the present invention.

[0049] Figure 23 Schematic structural view of the piston sleeve in the present invention.

[0050] Figure 24 Schematic working view of the force transmission pin on the piston core located within the piston sleeve in the present invention.

[0051] Figure 25 Schematic working view of the force transmission pin on the piston core abutting against the lower end face of the piston sleeve in the present invention.

[0052] Figure 26 Schematic working view of the force transmission pin compression ring abutting against the force transmission pin in the present invention.

[0053] Figure 27 Schematic working view of the piston engine in the present invention at the start of the exhaust stroke (end of the power stroke).

[0054] Figure 28 Schematic working view of the piston engine in the present invention at the end of the exhaust stroke.

[0055] Figure 29 Schematic working view of the position holding mechanism of the piston engine in the present invention at the end of the exhaust stroke.

[0056] Figure 30 Schematic working view of the piston engine in the present invention when the crank is at the zero-degree phase angle.

[0057] Figure 31 Schematic working view of the position holding mechanism of the piston engine in the present invention when the piston rod is at the top dead center.

[0058] Figure 32 Schematic working view of the piston engine in the present invention at the start of the intake stroke.

[0059] Figure 33 Schematic working view of the unlocking of the position holding mechanism of the piston engine in the present invention at the start of the intake stroke.

[0060] Figure 34 Schematic working view of the piston engine in the present invention when the piston core and the upper end face of the piston sleeve are flush during the intake stroke.

[0061] Figure 35 Schematic working view of the piston engine in the present invention at the end of the intake stroke.

[0062] Figure 36 Schematic diagram of the operation of the piston engine of the present invention at the end of the compression stroke.

[0063] Figure 37 Schematic diagram of the operation of the piston rod and the piston core of the piston engine of the present invention at the top dead center before the power stroke.

[0064] Figure 38 Schematic diagram of the operation of the piston engine of the present invention at the start of the power stroke.

[0065] Figure 39 Schematic diagram of the piston engine of the present invention when the upper end surfaces of the piston core and the piston sleeve are flush during the power stroke.

[0066] Figure 40 Schematic diagram of the operation of the piston engine of the present invention at the end of the power stroke.

[0067] Figure 41 Schematic diagram of the rotational angle position of the crank in the piston engine of the present invention.

[0068] Figure 42 Schematic diagram of the structure of another embodiment of the cylinder piston device of the present invention.

[0069] Figure 43 For Figure 42 Schematic diagram of the structure of the lower end side of the cylinder piston device.

[0070] Figure 44 For Figure 43 Cross-sectional view taken along the A-A direction in

[0071] Explanation of the reference numerals in the drawings

[0072] 1 Crank

[0073] 2 Connecting rod

[0074] 3 Linear slider

[0075] 4 Driven slider

[0076] 401 Driving boss

[0077] 402 Guide rail

[0078] 403 Limit block

[0079] 5 Sliding actuator

[0080] 501 Driving block

[0081] 501a Locking inclined surface

[0082] 501b Driving shaft hole

[0083] 501c Transition surface

[0084] 502 Drive bolt

[0085] 502a Drive shaft part

[0086] 503 First return spring

[0087] 6 Clutch mechanism

[0088] 601 Top block

[0089] 602 Second return spring

[0090] 603 Locking block

[0091] 604 Third return spring

[0092] 605 Action execution connecting rod

[0093] 606 Action execution swing arm

[0094] 606a Roller

[0095] 607 Action claw

[0096] 607a Trigger slope

[0097] 607b Slack surface

[0098] 608 Fixed limit rod

[0099] 609 Fourth return spring

[0100] 7 Position holding mechanism

[0101] 701 Fixed support

[0102] 701a Guide groove

[0103] 702 Guide wheel set

[0104] 703 Latch

[0105] 703a Latch shaft

[0106] 703b Top wheel

[0107] 703c Locking wheel

[0108] 704 Fifth return spring

[0109] 705 Locking block

[0110] 705a Locking block guide wheel

[0111] 706 Shift lever

[0112] ​

[0113] 708 Pushing arm

[0114] 708a Pushing wheel

[0115] 708b Lifting and pressing wheel

[0116] 708c Pushing rotating shaft

[0117] 709 Wedge block

[0118] 709a Wedge block inclined plane

[0119] 710 Guide frame

[0120] 710a Guide through hole

[0121] 711 Bracket

[0122] 711a Slide block square hole

[0123] 712 Action slide block

[0124] 712a Second cylindrical concave surface

[0125] 712b First cylindrical concave surface

[0126] 713 Action wheel

[0127] 714 First switching swing arm

[0128] 715 Switching connecting rod

[0129] 716 Second switching swing arm

[0130] 717 Lifting wheel

[0131] 718 Seventh return spring

[0132] 719 Rotating shaft frame

[0133] 720 Rotating shaft

[0134] 721 Smooth rod bolt

[0135] 722 Holding support plate

[0136] 8 Flexible connection assembly

[0137] 801 Adapter block

[0138] 802 Connection block

[0139] 9 Piston

[0140] 91 Piston sleeve

[0141] 91a Second limit stop surface

[0142] 91b Grade I sleeve section

[0143] 91c Grade II sleeve section

[0144] 92 Piston core

[0145] 92a First limit stop surface

[0146] 92b Force transmission pin hole

[0147] 92c Unlock block hole

[0148] 92d Grade I core section

[0149] 92e Grade II core section

[0150] 92f Grade III core section

[0151] 92g Inner piston ring groove

[0152] 10 Piston rod

[0153] 11 Cylinder

[0154] 11a Outer wall boss

[0155] 11b Intake hole

[0156] 11c Exhaust hole

[0157] 11d Combustion chamber

[0158] 11e Inter-stage stepped surface

[0159] 11f Unlock pin through-hole

[0160] 11g Locking pin through-hole

[0161] 11h Retaining pin through-hole

[0162] 11i Core inner hole

[0163] 11j Sleeve inner hole

[0164] 12 Force transmission pin pressing ring

[0165] 12a Annular inclined cutting surface

[0166] 13 Sleeve locking mechanism

[0167] 13a Force transmission plate

[0168] 13b Unlock pin

[0169] 13c Locking pin

[0170] 13d Retaining pin

[0171] 13e Locking spring

[0172] 13f guide post

[0173] 14 force transmission pin

[0174] 14a retracted inclined plane

[0175] 15 unlocking block

[0176] 15a unlocking inclined plane Detailed implementation manners

[0177] The following specific embodiments illustrate the implementation manners of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification.

[0178] It should be noted that the structures, ratios, sizes, etc. shown in the drawings of this specification are only used to cooperate with the content disclosed in the specification for those skilled in the art to understand and read, and are not used to limit the limiting conditions for the implementation of the present invention. Therefore, they do not have technical essential significance. Any modification of the structure, change of the proportional relationship, or adjustment of the size, without affecting the effects that the present invention can produce and the purposes that can be achieved, should still fall within the scope covered by the technical content disclosed in the present invention. At the same time, the terms such as "upper", "lower", "left", "right", "middle", etc. cited in this specification are only for the convenience of description and are not used to limit the scope of implementation of the present invention. The change or adjustment of their relative relationships, without substantial change in the technical content, should also be regarded as the scope within which the present invention can be implemented.

[0179] See Figures 1 to 41, the present invention provides a crank - connecting rod motion device, which includes a crank 1, a connecting rod 2, and a linear slider 3. One end of the connecting rod 2 is hinged to the crank 1. The linear slider 3 moves linearly in the up - and - down direction and is located above the crank 1. The device further includes a passive slider 4, a sliding actuator 5, a clutch mechanism 6, and a position - holding mechanism 7. The sliding actuator 5 is connected to the linear slider 3 and they move linearly synchronously. The passive slider 4 is hinged to the other end of the connecting rod 2. The clutch mechanism 6 is arranged between the passive slider 4 and the sliding actuator 5, and the clutch mechanism 6 has a transmission - connected state and a transmission - disconnected state. When the clutch mechanism 6 is in the transmission - connected state, the passive slider 4 establishes a motion connection with the sliding actuator 5 and moves up and down synchronously. When the clutch mechanism 6 is in the transmission - disconnected state, the passive slider 4 disconnects the motion connection with the sliding actuator 5, and the passive slider 4 can move linearly up and down relative to the linear slider 3. When the passive slider 4 reaches the upper limit position, the phase angle corresponding to the crank 1 is the zero - point phase angle, and a transmission - disconnected angle θ1 and a transmission - connected angle θ2 are respectively provided before and after the zero - point phase angle along the rotation direction. When the crank 1 rotates from the transmission - disconnected angle to the transmission - connected angle, the passive slider 4 first moves towards the upper limit position and then moves towards the lower limit position. During the process of the crank 1 rotating from the transmission - connected angle to the transmission - disconnected angle, the clutch mechanism 6 is in the transmission - connected state. During the process of the crank 1 rotating from the transmission - disconnected angle to the transmission - connected angle, the clutch mechanism 6 is in the transmission - disconnected state, and the linear slider 3 is located at its upper limit position. When the crank 1 is at the transmission - connected angle and the transmission - disconnected angle, the clutch mechanism 6 completes the state switch. When the crank 1 reaches the transmission - disconnected angle, the position - holding mechanism 7 is triggered to act and can lock the position of the linear slider 3. When the crank 1 reaches the transmission - connected angle, the position - holding mechanism 7 is triggered to act and releases the position lock of the linear slider 3.

[0180] The basic working principle of the crank - connecting rod motion device involved in the present invention is as follows: The crank 1 continuously rotates in a circular motion. Refer to Figure 41, and drives the passive slider 4 to move linearly up and down through the connecting rod 2. During the process of the crank 1 rotating from the transmission connection angle to the transmission disconnection angle, the clutch mechanism 6 is in the transmission connection state. At this time, a transmission connection is established between the passive slider 4 and the sliding actuator 5, and both the linear sliding member 3 and the sliding actuator 5 move linearly up and down synchronously with the passive slider 4. First, they move downward to their respective lower limit positions, and then move upward. When the crank 1 reaches the transmission disconnection angle, the clutch mechanism 6 switches to the transmission disconnection state. The linear sliding member 3 and the sliding actuator 5 reach their upper limit positions and no longer move upward with the passive slider 4. And the position holding mechanism 7 is triggered to act and can lock the position of the linear sliding member 3 to keep it at the upper limit position, while the crank 1 can continue to move towards the zero-degree phase angle. During this period, the passive slider 4 continues to move upward for a certain distance, that is, the moment when the passive slider 4 reaches its upper limit position is different from the moment when the linear sliding member 3 reaches the upper limit. When the crank 1 reaches the zero-degree phase angle, the connecting rod 2 and the crank 1 are collinear and in the same direction, which can also be called the top dead center position of the crank. The passive slider 4 reaches its upper limit position, and the crank 1 continues to rotate towards the transmission connection angle. The passive slider 4 starts to move downward. When the crank 1 reaches the transmission connection angle, the position holding mechanism 7 is triggered to act and releases the position lock on the linear sliding member 3, and the clutch mechanism 6 switches to the transmission connection state. At this time, if a downward force F is applied to the linear sliding member 3, since the crank 1 has rotated to the transmission connection angle, see Figure 32 , there is a certain angle between it and the zero-degree phase angle. The crank 1 has crossed the position collinear with the connecting rod 2, and the angle between the axis of the connecting rod 2 and the crank 1 is significantly beneficial to the conversion of force to torque. The corresponding force arm length is close to the length of the crank. The torque formed by the force F transmitted to the crank 1 through the connecting rod 2 is large, which can better drive the rotation of the crank 1.

[0181] Therefore, compared with the direct connection method between the connecting rod and the slider in the existing traditional crank and connecting rod mechanism, in the crank and connecting rod motion device of the present invention, a passive slider 4, a sliding actuator 5 and a clutch mechanism 6 are arranged between the connecting rod 2 and the linear sliding member 3 for connection, which can automatically disconnect or connect between the connecting rod 2 and the linear sliding member 3 according to the position of the crank 1. During the continuous rotation of the crank 1, in the region near the zero-degree phase angle 0°, the linear sliding member 3 can stay stationary at the upper limit position for a period of time. The crank and connecting rod motion device of the present invention can be used in similar occasions such as piston engines, see Figure 1 and Figure 12As shown, the linear slider 3 is connected to or integral with the piston rod 10. In this way, during the power stroke, when the crank 1 rotates to the transmission connection angle, it can be driven by the piston 9 to rotate. For the specific working principle, reference can be made to the description of the engine operation principle in the following text. Of course, the crank - connecting rod motion device of the present invention can also be applied to other similar occasions, such as in a hydraulic cylinder, or in occasions where the crank 1 is the driving part to drive the linear slider 3 to move (such as a compressor), and where the linear slider 3 needs to stay at the upper limit position for a period of time.

[0182] Refer to Figures 1 to 11 , the following further illustrates the crank - connecting rod motion device of the present invention with a specific embodiment:

[0183] In this embodiment, refer to Figure 1 、 Figure 2 and Figure 3 For convenience of description, the moving direction of the linear slider 3 is the up - and - down direction, the direction perpendicular to the up - and - down direction within the moving plane of the crank 1 is the left - and - right direction, and the axial direction of the crank 1 axis is the front - and - back direction. Also, the inner side is the side closer to the center line of the movement of the passive slider 4 (the movement track line of the hinge point with the connecting rod 2, which is also the axis of the piston 9 in the engine), and the other side is the outer side. As a preferred design, a driving boss 401 is fixedly provided on the passive slider 4. The sliding actuator 5 includes a driving block 501, a driving bolt 502, and a first return spring 503. The driving block 501 moves linearly in the up - and - down direction and is directly or indirectly connected to the linear slider 3, and the two move up and down synchronously. One end of the driving bolt 502 is hinged to the driving block 501, and the other end is the swinging end. The driving bolt 502 is located above the driving boss 401. Specifically, a driving shaft portion 502a is provided at one end of the driving bolt 502, and is installed in the driving shaft hole 501b on the driving block 501 through the driving shaft portion 502a, with stable installation. The first return spring 503 is installed on the driving block 501 and acts on the driving bolt 502. The first return spring 503 exerts an elastic force on the driving bolt 502 to drive the driving bolt 502 to swing downward until the swinging end presses against the driving boss 401. The driving bolt 502 and the first return spring 503 both move up and down with the driving block 501, that is, the sliding actuator 5 as a whole moves up and down.

[0184] In this embodiment, refer to Figure 4 、 Figure 5 and Figure 6, as a preferred design, the clutch mechanism 6 includes a top block 601, a locking block 603, a second return spring 602, a third return spring 604, an action execution component, and a trigger component. The top block 601, the locking block 603, the second return spring 602, the third return spring 604, and the action execution component are all installed on the passive slider 4 and can move up and down synchronously with the passive slider 4. The top block 601 is located above the driving boss 401 and on one side of the swinging end of the driving bolt 502. The top block 601 can linearly move relative to the passive slider 4 to approach or move away from the swinging end of the driving bolt 502. In this embodiment, the top block 601 moves in the left-right direction and is located inside the driving bolt 502. The second return spring 602 acts on the top block 601 and provides an elastic force to drive the top block 601 to move outward and press against the swinging end of the driving bolt 502. The locking block 603 can linearly move up and down relative to the passive slider 4, and when the locking block 603 moves, it can enter or leave the side of the top block 601 away from the driving bolt 502 through a guiding surface. Specifically, in this embodiment, the locking block 603 is located below the top block 601 and inside the top block 601. On the inner side of the top block 601 (the side away from the swinging end of the driving bolt 502) and the outer side of the locking block 603 (the side close to the top block 601), there is an inclined surface as the guiding surface. When the locking block 603 moves upward, the inclined surface on its outer side fits and contacts the inclined surface on the inner side of the top block 601, and it can smoothly insert and push the top block 601 to tightly press against the swinging end of the driving bolt 502. The more important function of this inclined surface is to facilitate the locking block 603 to slide out from the inner side of the top block 601 when moving downward. The third return spring 604 acts on the locking block 603 and provides an elastic force to drive the locking block 603 to enter the side of the top block 601 away from the driving bolt 502 (i.e., the inner side) and abut against it, that is, to drive the locking block 603 to move upward to push the top block 601 outward until it abuts against the swinging end of the driving bolt 502. The action execution mechanism is connected to the locking block 603 and is used to drive the up and down movement of the locking block 603. The trigger component cannot translate in the left-right direction. Specifically, it can be installed on a certain fixed seat near the upper limit position of the passive slider 4. When the crank 1 rotates from the transmission connection angle to the transmission disconnection angle, the locking block 603 abuts against the top block 601, and the swinging end of the driving bolt 502 abuts against both the top block 601 and the driving boss 401. See Figure 6The state shown, at this time, the locking block 603 abuts against the top block 601 under the elastic force of the third return spring 604, preventing the top block 601 from moving inward to separate from the swing end of the driving bolt 502. The swing end of the driving bolt 502 abuts against the lower driving boss 401 and the inner top block 601 at the same time, and is restricted from transmitting motion. Therefore, during movement, between the driving block 501 and the passive slider 4, force is transmitted through the driving bolt 502, the top block 601, and the driving boss 401 to ensure that the driving block 501 and the passive slider 4 move synchronously. That is, at this time, the clutch mechanism 6 is in a transmission connection state, and the linear sliding member 3, the sliding actuator 5, and the passive slider 4 move up and down linearly synchronously. When the crank 1 rotates to the transmission disconnection angle, the action execution assembly contacts the trigger assembly and acts, driving the locking block 603 away from the top block 601. Refer to Figure 5 The state shown, at this time, the locking block 603 no longer prevents the movement of the top block 601, and the top block 601 no longer prevents the swing end of the driving bolt 502 from swinging upward (i.e., Figure 5 rotating counterclockwise in the figure), so when the driving block 501 remains stationary with the linear sliding member 3, when the passive slider 4 continues to move upward, the driving boss 401 can push the driving bolt 502 to rotate, and the motion will no longer be transmitted to the driving block 501. The transmission between the passive slider 4 and the driving block 501 is disconnected. That is, at this time, the clutch mechanism 6 is in a transmission disconnection state, the passive slider 4 can move upward relative to the linear sliding member 3, the driving bolt 502 does not contact the top block 601, and the top block 601 is reset outward under the action of the second return spring 602. During the process of the crank 1 rotating to the transmission disconnection angle, the passive slider 4 reaches the upper limit position from moving upward and then changes to moving downward. The driving bolt 502 is reset and swings downward under the action of the first return spring 503 and contacts the top block 601. When the crank 1 is at the transmission connection angle, the swing end of the driving bolt 502 resumes contact with the upper side of the driving boss 401, the action execution assembly and the trigger assembly are disengaged, and the locking block 603 is reset under the elastic force of the third return spring 604 to the side away from the driving bolt 502 and abuts against the top block 601, restricting the position of the top block 601 from moving inward any further. The entire clutch mechanism 6 returns to Figure 6 The state shown, that is, it switches to the transmission connection state. At this time, when the crank 1 continues to rotate, the passive slider 4 can drive the linear sliding member 3 to move. In the transmission connection state, the passive slider can be driven by the linear sliding member to drive the crank to rotate.

[0185] In this embodiment, refer to Figure 4 、 Figure 5 and Figure 6, as an optimized design, the action execution mechanism of the clutch mechanism 6 includes an action execution swing arm 606 and an action execution link 605. The middle of the action execution swing arm 606 is hinged to the passive slider 4, one end thereof is a trigger action end, and the other end is hinged to one end of the action execution link 605. The other end of the action execution link 605 is hinged to the lock block 603; the trigger assembly includes an action claw 607 and a fixed limit rod 608 located above the action claw 607. The fixed limit rod 608 extends in the up and down direction. A downward trigger inclined surface 607a is provided on the action claw 607, and the trigger inclined surface 607a faces inward. The trigger inclined surface 607a can be a plane or a curved surface. When the passive slider 4 moves from the lower limit position to the upper limit position, the trigger action end of the action execution swing arm 606 can contact the trigger inclined surface 607a and then abut against the fixed limit rod 608. When the trigger action end of the action execution swing arm 606 moves along the trigger inclined surface 607a, the action execution swing arm 606 rotates and drives the lock block 603 to slide downward through the action execution link 605 to leave the top block 601, and the lock block 603 remains in the released state when the trigger action end abuts against the fixed limit rod 608. Specifically, in this embodiment, both the action claw 607 and the fixed limit rod 608 are located outside the passive slider 4 and the action execution swing arm 606. A roller 606a is provided on the trigger action end of the action execution swing arm 606 to contact the trigger inclined surface 607a, reducing friction and making the movement smoother. When the passive slider 4 moves from the lower limit position to the upper limit position, the roller 606a first contacts the trigger inclined surface 607a of the action claw 607. Under the action of the trigger inclined surface 607a, the action execution swing arm 606 rotates clockwise ( Figure 4 in the shown drawing), drives the lock block 603 to move downward through the action execution link 605 to leave the top block 601, and then the roller 606a enters the inner side of the fixed limit rod 608 and remains in contact. Refer to Figure 5 . The lock block 603 cannot be reset upward. When the passive slider 4 moves downward from the upper limit position, the roller 606a moves along the inner side of the limit rod 608, then leaves the fixed limit rod 608, abuts against the relaxation surface 607b of the action claw opened 607, and pushes the action claw 607 to swing downward clockwise, and finally disengages from the action claw 607. The action execution swing arm 606 can rotate smoothly automatically, and the lock block 603 can be reset smoothly. Refer to Figure 6 shown. Of course, in other embodiments, the action execution mechanism can also adopt other suitable transmission mechanisms, and the trigger assembly can also adopt other suitable adapted structures as long as the same functions can be achieved.

[0186] In this embodiment, further preferably, the action claw 607 is rotatably mounted and can swing up and down. The action claw 607 is provided with a slack surface 607b facing upward, and the slack surface 607b faces inward. The trigger assembly further includes a fourth return spring 609. The fourth return spring 609 acts on the action claw 607 and provides an elastic force to drive the action claw 607 to abut against the lower end of the fixed limit rod 608. In this way, when the passive slider 4 descends from the upper limit position to near the position of the action claw 607, when the roller 606a leaves the fixed limit rod 608 and contacts the slack surface 607b of the action claw 607, it can smoothly push the action claw 607 to swing downward ( Figure 6 in the clockwise direction shown in the drawing), so that the roller 606a and the passive slider 4 can smoothly descend, and when the lower side surface of the swing end of the driving bolt 502 is in contact with the upper side surface of the driving boss 401 and its inner side surface abuts against the outer side surface of the top block 601, the blocking of the action execution swing arm 606 can be smoothly released, so that the lock block 603 can be reset more smoothly. After the lock block 603 leaves, the action claw 607 is reset to abut against the lower end of the fixed limit rod 608 under the action of the fourth return spring 609, waiting for the next trigger action. Of course, in other embodiments, the action claw 607 can also be fixedly installed, and the inner edge of the trigger inclined surface 607a is smoothly connected to the inner side edge of the fixed limit rod 608, so that the roller 606a can smoothly move between the two, as long as it is ensured that the lock block 603 can smoothly wedge into the inner side of the top block 601 to prevent the driving bolt 502 from rotating counterclockwise when the inner side surface of the swing end of the driving bolt 502 abuts against the outer side surface of the top block 601.

[0187] In this embodiment, referring to Figure 2 、 Figure 3 and Figure 4 , as a preferred design, a limit block 403 and a guide rail 402 are fixedly arranged on the passive slider 4. The limit block 403 is located above the driving boss 401, and a guiding groove extending linearly left and right is formed between the two. The top block 601 is located in the guiding groove and can only translate left and right, and the top block 601 can be in contact with the limit block 403 and the driving boss 401. The guide rail 402 is located at the middle position of the limit block 403. The second return spring 602 is located between the top block 601 and the guide rail 402. The lock block 603 is also located between the top block 601 and the guide rail 402. The lock block 603 is installed on the guide rail 402 and can only move linearly in the up and down direction under the limitation of the guide rail 402.

[0188] In this embodiment, referring to Figure 7 、 Figure 8 and Figure 9, as a preferred design, the driving block 501 of the sliding actuator 5 is provided with a downward locking inclined surface 501a and a transition surface 501c connected to the upper side of the locking inclined surface 501a. The locking inclined surface 501a can be a plane or a curved surface. The position holding mechanism 7 includes a fixed support 701, a latch 703, a clamping block 705, a lever 706, a pushing arm 708, a fifth return spring 704, a sixth return spring 707, a holding plate 722, a wedge block assembly, and an extending trigger structure. The fixed support 701 is located between the air cylinder and the crankshaft bearing seat, and its length covers the upper limit to the lower limit range of the passive slider 4, and becomes the limit of the sliding actuator 5 in the direction perpendicular to its own movement trajectory. The latch 703 is rotatably mounted on the fixed support 701, and is provided with a top-holding portion and a rotation-blocking portion thereon. Preferably, the top-holding portion includes a top wheel 703b, and the rotation-blocking portion includes a locking wheel 703c, which can reduce the frictional force during contact. The fifth return spring 704 is disposed between the fixed support 701 and the latch 703, and applies an elastic force to drive the latch 703 to rotate until the top wheel 703b of the top-holding portion is located at the position of the locking inclined surface 501a of the driving block 501 when it is in the upper limit position, and its purpose is to press on the locking inclined surface 501a. The clamping block 705 is installed in a guide groove 701a extending in the vertical direction on the fixed support 701 and can move linearly up and down in the guide groove 701a. The lever 706 is fixed to the clamping block 705, specifically fixed to the upper side end of the clamping block 705, and the two can also be integrated. The sixth return spring 707 is disposed on the fixed support 701 and applies an elastic force to the clamping block 705 to drive it downward to abut against the locking wheel 703c of the latch 703 and prevent the latch 703 from rotating. Preferably, a clamping block guide wheel 705a is provided on the clamping block 705 to contact the guide groove 701a, and the sixth return spring 707 abuts against the upper end or the lever 706 on the upper side of the clamping block 705. The middle of the pushing arm 708 is hinged to the fixed support 701, and its first end is located inside the lever 706, and the second end is used to contact the wedge block 709. Preferably, the pushing arm 708 is installed through a pushing rotating shaft 708c and can rotate. A pushing wheel 708a is provided at the first end to contact the lever 706, and a lifting and pressing wheel 708b is provided at the second end to contact the wedge block 709, which can reduce the frictional resistance. The wedge block assembly is installed on the passive slider 4 and includes a wedge block 709 and a telescopic driving portion for driving the wedge block 709 to extend or retract. Specifically, in this embodiment, refer to Figure 7, the wedge block 709 can move relative to the passive slider 4 in a direction perpendicular to the movement track of the passive slider 4. When moving outward and approaching the push arm 708, it is in the extended state. When the wedge block 709 in the extended state moves up and down, it can touch the lifting and pressing wheel 708b. When moving inward and away from the push arm 708, it is in the retracted state. In this state, the wedge block cannot touch the lifting and pressing wheel 708b when moving up and down. The holding plate 722 is connected to the driving block 501 and is located above the transition surface 501c. Specifically, the holding plate 722 is directly connected to the driving block 501 or connected to at least one component in the flexible connection assembly 8, and the holding plate 722 becomes an extension of the transition surface 501c of the driving block 501 in the upward limit direction, or slightly higher than the transition surface 501c of the driving block 501 and extends in the upward limit direction. There may be functional recesses around the holding plate 722. The holding plate 722 is located outside the wedge block 709 in the extended state. When the linear slider 3 is at its upper limit position, the top wheel 703b of the abutting holding portion of the latch 703 presses on the locking inclined surface 501a, and when the passive slider 4 is at its upper limit position, the wedge block 709 is located above the second end of the push arm 708. When the passive slider 4 moves downward from the upper limit position, the wedge block 709 in the extended state will push the second end of the push arm 708 to rotate, see Figure 31 and Figure 33 As shown, when the push arm 708 rotates, the first end will push the lever 706 to move the latch 705 to move away from preventing the rotation of the latch 703. When the holding plate 722 moves downward with the driving block 501, it can successively or simultaneously abut against the top wheel 703b of the abutting holding portion and the lifting and pressing wheel 708b at the second end of the push arm 708 to prevent the latch 703 from resetting and rotating and the latch 705 from resetting and moving downward, ensuring the smooth movement of the driving block 501 and avoiding the untimely locking action of the position holding mechanism 7. The extension trigger structure is fixedly arranged near the upper limit position of the passive slider 4. When the linear slider 3 is at its upper limit position and the passive slider 4 reaches its upper limit position, the extension trigger structure triggers the telescopic drive portion to move downward relative to the passive slider 4 to the in-place position so that the wedge block 709 is in the extended state. Preferably, the position holding mechanism 7 further includes a retraction trigger structure, which can be fixedly arranged near the lower limit position of the passive slider 4. After the wedge block 709 moves downward with the passive slider 4 to be located below the push arm 708 and reaches the lower limit position, the retraction trigger structure triggers the telescopic drive portion to move upward relative to the passive slider to the in-place position so that the wedge block 709 is in the retracted state.

[0189] The working principle of the position holding mechanism 7 in this embodiment is as follows: During the synchronous upward movement of the passive slider 4 and the linear slider 3, the top wheel 703b on the latch 703 and the lifting and pressing wheel 708b of the push arm 708 first come into contact with the holding plate 722, see Figure 27In the state shown, the latch top wheel 703b then disengages from the holding pallet 722 and instead contacts the transition surface 501c on the drive block 501, while the lifting and pressing wheel 708b continues to contact the holding pallet 722. As a result, the latch 703 and the pushing arm 708 are restricted from resetting before the sliding actuator 5 reaches the top dead center. Also, when the lifting and pressing wheel 708b abuts against the holding pallet 722, the latch block 705 separates from the top wheel 703b, not obstructing the reset rotation of the latch 703 under the action of the fifth return spring 704. At this time, the wedge block 709 is already in the retracted state, avoiding contact with the lifting and pressing wheel 708b on the pushing arm 708. The guide wheels 705a on the latch block 705 are arranged on both sides of the latch block and are always located in the guide grooves provided along the vertical direction on the upper edge of the fixed support 701 without contacting the top wheel 703b. The inner side surface and the inner part of the lower end of the latch block 705 are the parts that contact the top wheel 703b of the top-holding part that abuts against the latch 703. Before the crank 1 reaches the transmission disconnection angle, that is, before the linear sliding member 3 reaches its upper extreme position, the top wheel 703b on the latch 703 first contacts the holding pallet 722, then contacts the transition surface 501c on the drive block 501, and finally, when the linear sliding member 3 reaches its upper extreme position, the top wheel 703b presses tightly against the locking inclined surface 501a, and the lifting and pressing wheel 708b of the pushing arm 708 disengages from the contact with the holding pallet 722, no longer preventing the downward movement of the lever 706 and the latch block 705. Therefore, the latch block 705 can smoothly reset downward under the action of the sixth return spring 707 to contact the locking wheel 703c, causing the latch 703 not to rotate. Thus, the top wheel 703b cannot leave the locking inclined surface 501a, and the top wheel 703b remains pressed tightly against the locking inclined surface 501a, thereby preventing the drive block 501 and the linear sliding member 3 from descending and keeping them in the upper extreme position, see Figure 29 the state shown. Then the crank 1 reaches the zero-degree phase angle, and the passive slider 4 reaches its upper extreme position. The telescopic drive part of the wedge block assembly on the passive slider 4 moves downward relative to the passive slider 4 to the in-place position due to the triggering action of the triggering structure of the extending part, and the telescopic drive part makes the wedge block 709 in the extended state. Then the passive slider 4 drives the wedge block assembly to descend together. Preferably, a wedge block inclined surface 709a is provided on the lower side of the wedge block 709. The wedge block 709 contacts the lifting and pressing wheel 708b through the wedge block inclined surface 709a and pushes the pushing arm 708 to rotate, see Figure 33As shown, when the push arm 708 rotates, it drives the lever 706 and the latch 705 to move upward through the push wheel 708a. And when the crank 1 is at the transmission connection angle, the latch loses its restraint on the locking wheel 703c. Therefore, the latch 705 loses its restraint on the rotation of the lock bolt 703. At this time, when the driving block 501 continues to move downward, the lock bolt 703 can be driven by the locking inclined surface 501a to rotate against the elastic force of the fifth return spring 704. That is, the lock bolt 703 no longer prevents the driving block 501 from moving downward, thus realizing the automatic release of the position limitation of the position holding mechanism 7 on the linear sliding member 3. Then, during the process of the driving block 501 and the passive slider 4 moving downward to the lower limit position together, the top wheel 703b of the lock bolt 703 moves from the locking inclined surface 501a to the transition surface 501c, and then contacts the outer side surface of the holding support plate 722. The lifting and pressing wheel 708b of the push arm 708 moves from the wedge block 709 to contact the outer side surface of the holding support plate 722. The holding support plate 722 prevents the lock bolt 703 from resetting and rotating, and prevents the latch 705 from resetting and moving downward. When the passive slider 4 reaches its lower limit position, the retracting trigger structure triggers the telescopic drive part to move upward relative to the passive slider 4 to the in-place position, so that the wedge block 709 is in the retracted state. Then the passive slider 4 and the linear sliding member 3 move upward synchronously, and the crank and connecting rod motion device repeats the above process, moving in a cycle.

[0190] In this embodiment, referring to Figure 9 、 Figure 10 and Figure 11, Further preferably, the telescopic driving part of the wedge block assembly includes a bracket 711, a guide frame 710, an action slider 712, a passive action part, and a switching transmission structure. The bracket 711 is fixed on the passive slider 4, the guide frame 710 is fixed to the bracket 711, the wedge block 709 is installed in the guide through hole 710a in the guide frame 710 and can move linearly outwards or retract. The action slider 712 is installed in the slider square hole 711a in the bracket 711 and can move linearly up and down in the bracket 711 along the slider square hole 711a. The action slider 712 is provided with an extending connection structure and a retracting connection structure located below the extending connection structure. The switching part is installed on the bracket 711 and is used for movingly connecting with the extending connection structure or the retracting connection structure. The switching transmission structure connects the passive action part and the wedge block 709. When the action slider 712 moves downwards relative to the bracket 711, the passive action part moves to the position of the extending connection structure, and the switching transmission structure drives the wedge block 709 to change to the extending state. When the action slider 712 moves upwards relative to the bracket 711, the passive action part moves to the position of the retracting connection structure, and the wedge block 709 changes to the retracting state; the extending trigger structure and the retracting trigger structure respectively include an extending upper boss (not shown in the drawings) and a retracting lower boss (not shown in the drawings) which are respectively fixedly arranged near the upper limit position and the lower limit position of the passive slider 4; the linear sliding part 3 is located at the upper limit position, and when the passive slider 4 moves upwards to its upper limit position, the upper end of the action slider 712 abuts against the extending upper boss. When the wedge block assembly moves downwards with the passive slider 4 to its lower limit position, the lower end of the action slider 712 abuts against the retracting lower boss.

[0191] In this embodiment, refer to Figure 9 , Figure 10 and Figure 11, Further, the extending connection structure and the retracting connection structure on the action slider 712 respectively include a first cylindrical concave surface 712b and a second cylindrical concave surface 712a, and the first cylindrical concave surface 712b and the second cylindrical concave surface 712a are connected by an inclined surface, that is, there is a height difference between the two. The passive action member is an action wheel 713. The action wheel 713 can be placed in the first cylindrical concave surface 712b and the second cylindrical concave surface 712a, and the action wheel 713 can move between the two through the inclined surface therebetween. Preferably, the diameter of the action wheel 713, the diameter of the first cylindrical concave surface 712b, and the diameter of the second cylindrical concave surface 712a are all the same, and the action wheel 713 can be in a stable state in the first cylindrical concave surface 712b and the second cylindrical concave surface 712a. The switching transmission structure includes a first switching swing arm 714, a second switching swing arm 716, a switching link 715, and a lifting wheel 717. The middle parts of the first switching swing arm 714 and the second switching swing arm 716 are rotatably mounted on the bracket 711. Specifically, a rotating shaft frame 719 is fixed on the bracket 711, and the first switching swing arm 714 and the second switching swing arm 716 are respectively mounted on the rotating shaft frame 719 through a rotating shaft 720 and can rotate smoothly. One end of the first switching swing arm 714 is connected to the action wheel 713, and the other end is hinged to one end of the switching link 715. The other end of the switching link 715 is hinged to one end of the second switching swing arm 716. The other end of the second switching swing arm 716 is connected to the lifting wheel 717. The lifting wheel 717 abuts against the end (i.e., the inner end) of the wedge 709 away from the pushing arm 708. When the action wheel 713 moves from the second cylinder to the first cylindrical concave surface 712b, the lifting wheel 717 jacks up the wedge 709 to the extended state; the wedge assembly further includes a seventh return spring 718 mounted on the bracket 711. The seventh return spring 718 is specifically mounted on a pin or a smooth rod bolt 721 fixed to the guide frame 710. The seventh return spring 718 acts on the wedge 709 to provide an elastic force to drive the wedge 709 to move inward and reset to the retracted state. Of course, in this embodiment, the extending connection structure and the retracting connection structure on the action slider 712, as well as the passive action member, are not limited to the above forms, and other suitable structural forms can also be adopted. At the same time, the switching transmission structure is not limited to the above structural form, as long as the passive action member generates a displacement when moving and switching between the extending connection structure and the retracting connection structure, and this displacement can be transmitted to the wedge 709 through a suitable switching transmission structure to drive the wedge 709 to move towards or away from the pushing arm 708.

[0192] Preferably, in this embodiment, a ball spring pin (a conventional structure) is installed on the action slider 712 and is engaged with the pin hole on the bracket 711. When the action slider 712 moves to the position where the action wheel 713 is located in the first cylindrical concave surface 712b or the second cylindrical concave surface 712a, the ball spring pin just extends into the pin hole, restricting the action slider 712 from shaking up and down relative to the bracket 711. Only when the action slider 712 abuts against the protruding upper boss and the retracting lower boss to generate sufficient pressure can the elastic force of the ball spring pin be overcome, and the ball spring pin is disengaged from the pin hole, so that the action slider 712 can move relative to the bracket 711.

[0193] The working principle of the wedge block assembly in this embodiment is as follows: when the wedge block assembly moves to its upper limit position with the passive slider 4, the upper end of the action slider 712 abuts against the protruding upper boss, and the action slider 712 moves downward relative to the bracket 711. The action wheel 713 moves from the second cylindrical concave surface 712a to the first cylindrical concave surface 712b. Refer to Figure 10 As shown, at this time, the action wheel 713 has a displacement in the left - right direction. The action wheel 713 drives the lifting wheel 717 to move a certain distance in the left - right direction toward the pushing arm 708 through the first switching swing arm 714, the switching link 715, and the second switching swing arm 716. The lifting wheel 717 lifts the wedge block 709 to move it toward the pushing arm 708, and it is in the extended state and remains so. When the wedge block assembly moves to its lower limit position with the passive slider 4, the lower end of the action slider 712 abuts against the retracting lower boss, and the action slider 712 moves upward relative to the bracket 711. The action wheel 713 moves from the first cylindrical concave surface 712b to the second cylindrical concave surface 712a. The action wheel 713 drives the lifting wheel 717 to move a certain distance in the left - right direction away from the pushing arm 708 through the first switching swing arm 714, the switching link 715, and the second switching swing arm 716 to achieve reset. At this time, the wedge block 709 moves away from the pushing arm 708 under the action of the seventh reset spring 718 and moves to abut against the lifting wheel 717 again, resetting to the retracted state and remaining so until the wedge block assembly moves to its upper limit position again with the passive slider 4 and switches to the extended state again.

[0194] In this embodiment, the telescopic driving part of the wedge block assembly, as well as the extending trigger structure and the retracting trigger structure, all adopt a pure mechanical structure, which can achieve automatic triggering and switching, and has the advantages of stable and reliable structure. Of course, in the present invention, the telescopic driving part, the extending trigger structure and the retracting trigger structure are not limited to the above forms, and other structural forms can be adopted. Other pure mechanical structural forms can be adopted, and in some cases, an electronic driving form can also be adopted. For example, the extending trigger structure and the retracting trigger structure can adopt limit switches, infrared position detectors, etc., which can detect that the passive slider 4 reaches the upper limit position and the lower limit position, and send out signals, and control the action of the telescopic driving part according to the signals to drive the wedge block 709 to extend or retract. Among them, the telescopic driving part can adopt an electric driving form, such as a motor, an electric cylinder, etc.

[0195] In this embodiment, referring to Figure 1 and Figure 2 , as a preferred design, the position holding mechanism 7 further includes a guide wheel group 702. The guide wheel group 702 includes a plurality of guide wheels arranged linearly in the up and down direction. The inner side of the driving block 501 abuts against the passive slider 4, and the outer side of the driving block 501 can abut against the guide wheels when it moves downward. Specifically, in this embodiment, the guide wheel group 702 is installed on the fixed support 701 and is located below the latch 703. The inner side of the driving block 501 always abuts against the passive slider 4 through the contacting plane or is separated by a small gap. When the driving block 501 moves downward from its upper dead point, after the driving block 501 disengages from the latch 703, it abuts against the guide wheel group through the outer transition surface 501c. By the restraining effect of the guide wheel group on the driving block 501, it plays a role in offsetting the lateral force generated by the link 2 on the driving block 501 through the passive slider 4, making the movement more stable and reducing the friction force.

[0196] Of course, in the present invention, the position holding mechanism 7 is not limited to the structure in the above example, and other existing suitable structures can also be adopted, which can automatically trigger the locking action to lock the sliding actuator located at the upper limit position according to the position of the sliding actuator 5, and can automatically release the locking action according to the position when the passive slider 4 moves downward. For example, the above-mentioned limit switches, infrared position detectors, etc. can be used to determine the locking action and unlocking action by detecting the position.

[0197] As a preferred design, in this embodiment, referring to Figure 1 and Figure 2, the driving block 501 and the linear slider 3 are connected by a flexible connection assembly 8. The flexible connection assembly 8 includes a connection block 802 and a transfer block 801. The connection block 802 is pivotally connected to the linear slider 3, and the rotation axis is perpendicular to the rotation plane of the crank 1, that is, in the front-rear direction. The upper end of the transfer block 801 is pivotally connected to the connection block 802, and the lower end is pivotally connected to the driving block 501. The rotation axis between the transfer block 801 and the connection block 802 is perpendicular to the moving direction of the linear slider 3 and perpendicular to the rotation axis between the connection block 802 and the linear slider 3, that is, in the left-right direction. The rotation axis between the transfer block 801 and the driving block 501 is parallel to the rotation axis between the connection block 802 and the linear slider 3, that is, in the front-rear direction. Through the flexible connection assembly 8, the driving block 501 and the linear slider 3 are fixed in the up-down direction, but the two can have a small-angle relative rotation space in two directions. The flexible connection assembly 8 plays a role in position compensation. In a piston engine, it can avoid the situation where the driving block 501 is jammed due to the deviation of the parallelism of relevant components relative to the axis of the piston 9 during manufacturing and installation.

[0198] As a preferred design, in this embodiment, refer to Figure 1 and Figure 12 , two sliding actuators 5 and clutch mechanisms 6 in the crank connecting rod motion device can be provided and symmetrically arranged on the left and right sides of the motion center line of the passive slider 4. When in a piston engine, that is, symmetric about the axis of the piston 9. Correspondingly, corresponding structures are provided on both the left and right sides of the passive slider 4 to cooperate with the sliding actuator 5 and the clutch mechanism 6. The position holding mechanism 7 is also provided in two and symmetrically arranged on the left and right sides of the motion center line of the passive slider 4 for respectively locking the positions of the driving blocks 501 of the two sliding actuators 5. The wedge block assemblies of the two position holding mechanisms 7 can share a telescopic driving part, refer to Figure 9 , and simultaneously drive the extension and retraction of the two wedge blocks 709. Correspondingly, the flexible connection assembly 8 includes two transfer blocks 801, refer to Figure 1 and Figure 2 , the two transfer blocks 801 are respectively connected to the two driving blocks 501. The connection block 802 is one and is V-shaped and is simultaneously connected to the two transfer blocks 801. By adopting this symmetric setting method, the connection between the connecting rod 2 and the bracket 711 of the passive slider 4 is more stable and reliable, and the force transmission is more uniform. The position locking effect of the position holding mechanism 7 on the sliding actuator 5 and the linear slider 3 is also more stable and reliable. Two driving bolts 502 can also be symmetrically arranged on the front and rear of each driving block 501, and corresponding components and mechanisms related to their action and rest, such as a return spring, a top block 601, a lock block 603, and an action execution mechanism, etc., are also correspondingly provided.

[0199] The present invention also provides a power device, refer toFigure 12 , including a cylinder piston device, which includes a cylinder 11, a piston 9 located in the cylinder 11, and a piston rod 10 connected to the piston 9. It also includes the above-mentioned crank connecting rod motion device, and the linear sliding member 3 of the crank connecting rod motion device is fixedly connected to or integrated with the piston rod 10. The axes of the piston 9 and the piston rod 10 are both in the up and down direction, coinciding with or parallel to the motion center line of the passive slider 4, and the motion direction of the linear sliding member 3 is the same as that of the piston rod 10.

[0200] The power device of the present invention can have the piston 1 as the active moving part and the crank as the passive moving part. In this case, the power device can be a piston engine (internal combustion engine), a hydraulic power cylinder, etc. It can also have the crank as the active moving part and the piston 1 as the passive moving part. In this case, the power device can be a compressor, an oil pump, etc. When the power device of the present invention is a piston engine, it also includes existing structures such as an intake valve, an exhaust valve, and an ignition device when necessary. A combustion chamber 11d is provided at the top inside the cylinder 11, and an intake hole 11b, an exhaust hole 11c, and a spark plug hole are also provided at the top of the cylinder 11 for installing the intake valve, the exhaust valve, and the spark plug for ignition respectively.

[0201] The following further illustrates the cylinder piston device in the power device of the present invention with two embodiments;

[0202] First embodiment of the cylinder piston device:

[0203] As a preferred design, in this embodiment, participate Figure 16 , Figure 18 and Figure 19, in the cylinder 11, an inner core hole 11i and an N-stage sleeve inner hole 11j are successively arranged from top to bottom, where the number of stages N = 1. The cross-section of the inner core hole 11i to the sleeve inner hole 11j increases successively, so that an inter-stage stepped surface 11e is formed between the inner core hole 11i and the sleeve inner hole 11j. The piston 9 successively includes a piston core 92 and an N-stage piston sleeve 91 from inside to outside, the number of stages N = 1. The piston sleeve 91 is sleeved on the piston core 92 and can move relatively up and down. An inner piston ring (not shown in the drawing) is arranged between the piston core 92 and the piston sleeve 91. There is a certain axial frictional resistance between the piston core 92 and the piston sleeve 91 through the inner piston ring. The lower end of the piston core 92 is connected to the piston rod 10. A first limit stop surface 92a is arranged on the piston core 92, and a second limit stop surface 91a is arranged on the piston sleeve 91. The piston core 92 can move upward relative to the piston sleeve 91 until the first limit stop surface 92a abuts against the second limit stop surface 91a. When they abut, the upper end surface of the piston core 92 preferably extends out of the upper end surface of the piston sleeve 91. When the piston core 92 is at its top dead center, the upper end of the piston core 92 is located in the inner core hole 11i, and the upper end of the piston sleeve 91 is respectively located in the sleeve inner hole 11j. And there is a certain gap between the upper end of the piston sleeve 91 and the inter-stage stepped surface 11e on the upper end side of the sleeve inner hole 11j to avoid collision. At this time, the first limit stop surface 92a and the second limit stop surface 91a of the piston core 92 and the first-stage piston sleeve 91 abut against each other.

[0204] In this embodiment, the cylinder piston device further includes a sleeve locking mechanism 13, a force transmission mechanism, and a force transmission release mechanism. A force transmission mechanism is provided on the piston core 92. The force transmission mechanism includes a force transmission pin 14 disposed in a force transmission pin hole 92b formed on the outer side surface of the piston core 92 or the piston sleeve 91, and a force transmission elastic structure acting on the force transmission pin 14. The force transmission pin 14 can move in the force transmission pin hole 92b to extend out or retract into the force transmission pin hole 92b. The force transmission elastic structure (not shown in the drawings) is installed in the piston core 92, specifically, it can be in the force transmission pin hole 92b or inside the piston core 92, and applies an elastic force to the force transmission pin 14 to drive the force transmission pin 14 to move outward, so that the force transmission pin hole 92b extends out of the force transmission pin hole 92b when not under pressure. When the first limit stop surface 92a of the piston core 92 abuts against the second limit stop surface 91a on the first-stage piston sleeve 91, the force transmission pin 14 on the piston core 92 is located above the lower end surface of the piston sleeve 91. Specifically, the force transmission pin 14 can be partially or entirely located above the lower end surface of the piston sleeve 91. At this time, the force transmission pin 14 partially or entirely enters the inner cavity of the piston sleeve 91. The axis of the force transmission pin hole 92b preferably extends along the radial direction of the piston core 92. When the piston core 92 reaches the top dead center, the position of the piston sleeve 91 can be locked by the sleeve locking mechanism 13, so that the piston sleeve 91 cannot move downward. When the piston core 92 moves downward from its top dead center until the upper end of the force transmission pin 14 thereon reaches the lower end surface of the first-stage piston sleeve 91, the sleeve locking mechanism 13 releases the locking of the piston sleeve 91. Therefore, the force transmission pin 14 can extend out of the force transmission pin hole 92b and abut against the lower end surface of the piston sleeve 91 to achieve force transmission between the piston sleeve 91 and the piston core 92. When the piston core 92 moves downward to its bottom dead center, the force transmission release mechanism contacts the force transmission pin 14 in the extended state and compresses the force transmission pin 14 into the force transmission pin hole 92b, so that it no longer extends outside the circumferential surface of the piston core 92.

[0205] The basic working principle of the cylinder piston device in this embodiment is as follows: The piston core 92 and the inner piston ring of the piston sleeve 91 play a sealing role to prevent gas leakage between them. When a certain relative axial pressure is applied to the piston core 92 and the piston sleeve 91, when overcoming the frictional resistance formed between the piston core 92 and the piston sleeve 91 through the inner piston ring, the piston core 92 and the piston sleeve 91 can produce relative axial movement. When no relative axial pressure is applied or the pressure is not enough to overcome the frictional resistance and the piston sleeve is not blocked, the piston core 92 and the piston sleeve 91 can also achieve synchronous movement through the frictional resistance. When the piston core 92 and the piston sleeve 91 move synchronously downward, the force is transmitted by the force transmission pin 14 abutting against the lower edge of the piston sleeve 91. When moving upward, the force is transmitted by the first limit stop surface 92a abutting against the second limit stop surface 91a. If it is worried that the gas pressure acting on the piston sleeve 91 during the intake stroke is not enough to press it tightly against the force transmission pin 7, resulting in the situation that its downward movement is slower than that of the piston core 92, a structure for preventing the piston core 92 from slipping out of the lower end of the piston sleeve 91 can be added at the lower end face of the piston sleeve 91 and the appropriate position of the piston core, so that the piston core 11 drives the piston sleeve 12 to move synchronously. Preferably, the upper end face area of the piston core 92 is smaller than the upper end face area of the piston sleeve 91. It can also be the opposite or equal situation for a unique engine power characteristic curve, that is, the upper end face area of the piston core 92 is greater than or equal to the upper end face area of the piston sleeve 91. When the piston 9 moves downward, the piston sleeve 91 is pressed tightly against the force transmission pin 14 extending out of the piston core 92 under the action of the gas pressure in the cylinder 4, and the gas pressure is transmitted to the piston 92 and moves together with the piston core 92. If it is worried that the gas pressure acting on the piston sleeve 91 during the intake stroke is not enough to press it tightly against the force transmission pin 14, resulting in the situation that the movement speed of the piston sleeve 91 is slower than that of the piston core 92, a lower limit structure for preventing the piston core 92 from slipping out of the lower end of the piston sleeve 91 can be added at the lower end face of the piston sleeve 91 and the appropriate position of the piston core. When the piston core 92 moves downward relative to the piston sleeve 91, it will drive the piston sleeve 91 to move downward through the lower limit structure, ensuring that the piston core 92 drives the piston sleeve 91 to move synchronously downward.

[0206] When the cylinder piston device in this embodiment is adopted, during the power stroke, in the first stage, the piston sleeve 91 remains stationary while the piston core 92 moves first, and then in the second stage, the piston sleeve 91 and the piston core 92 move downward synchronously. Therefore, when the gas pressure is the highest, the force is transmitted through a partial cross-section (the cross-section part of the piston core 92) and is transmitted through the piston rod 10 and finally transmitted to the crank 1. In the first stage, the driving torque is controlled within an appropriate range to reduce the impact. By selecting the cross-sectional area of the piston core 92, the upper limit of the gas driving force received by the piston core 92 can be controlled, so as to achieve the purpose of controlling the driving torque generated on the crankshaft in this stage. For example, the lower limit of the driving torque generated by the force on the core piston 9 is not lower than the peak torque of a traditional internal combustion engine of the same specification, and its upper limit is controlled within a reasonable value. The gas pushes the piston core 92 to move a certain distance to expand. In the second stage, the entire cross-section at the top of the piston 9 bears the gas pressure. At this time, because the crank 1 rotates by a certain angle, the moment formed by the thrust transmitted from the piston 9 to the crank 1 through the piston rod 10 and the crank 1 is large. Although the pressure decreases at this time, compared with the traditional integral piston 9, when the angle of the crank 1 is the same, the gas pressure received by the piston 9 is greater, and the moment transmitted to the crank 1 is greater, so as to better drive the crank 1 to rotate. It can continue to maintain the torque not lower than the lower limit (the peak torque of the traditional engine) within a relatively large subsequent rotation angle range of the crank 1, that is, the maximum value of the torque is appropriately controlled.

[0207] See Figure 16 , Figure 20 and Figure 21, in the cylinder piston device of this embodiment, as a preferred design, the cylinder 11 is provided with an unlocking pin through hole 11f, a retaining pin through hole 11h, and a locking pin through hole 11g. The retaining pin through hole 11h is located below the locking pin through hole 11g, and the locking pin through hole 11g is located between the retaining pin through hole 11h and the unlocking pin through hole 11f, close to the locking pin through hole 4f. The sleeve locking mechanism 13 includes a force transmission plate 13a, a locking elastic structure, an unlocking pin 13b, a retaining pin 13d, and a locking pin 13c. The unlocking pin 13b, the retaining pin 13d, and the locking pin 13c are respectively located in the unlocking pin through hole 11f, the retaining pin through hole 11h, and the locking pin through hole g. The outer ends of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c are all connected to the force transmission plate 13a and move with the force transmission plate 13a. The locking elastic structure applies an elastic force to the force transmission plate 13a to drive the force transmission plate 13a to press against the outer wall of the cylinder 11. At this time, the inner ends of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c all extend into the cylinder 11. When the force transmission plate 13a approaches or moves away from the cylinder 11, the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c can synchronously extend or retract into the inner wall of the cylinder 11. When the piston sleeve 91 is at the top dead center, the locking pin 13c abuts against the lower end surface of the piston sleeve 91. The piston core 92 is provided with an unlocking block 15, specifically arranged in the unlocking block hole 92c on the outer wall of the piston core 92, and moves up and down synchronously with the piston core 92. The lower side of the unlocking block 15 is provided with an unlocking inclined surface 15a, which can be a flat surface or a curved surface. When the piston core 92 is at the top dead center, the unlocking inclined surface 15a is located above the unlocking pin 13b. When the unlocking block 15 moves downward, the unlocking inclined surface 15a can contact the unlocking pin 13b and drive the unlocking pin 13b to move outward until it retracts into the inner wall of the cylinder 11. At this time, the force transmission plate 13a is also driven, and the retaining pin 13d and the locking pin 13c also synchronously retract into the inner wall of the cylinder 11. When the piston sleeve 91 leaves its top dead center, at least one of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c abuts against the outer peripheral surface of the piston sleeve 91.

[0208] The working principle of the sleeve locking mechanism 13 in this embodiment is as follows: When the piston sleeve 91 and the piston core 92 are both at their top dead centers, the force transmission plate 13a presses on the piston sleeve 91. The inner ends of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c all extend into the cylinder 11. The locking pin 13c abuts against the lower end surface of the piston sleeve 91, and the piston sleeve 91 cannot move downward and will be locked at the top dead center. See Figure 4Among them, the unlocking pin 13b is preferably arranged near the locking pin 13c. When the piston core 92 descends from the top dead center, the unlocking inclined surface 15a of the unlocking block 15 contacts the unlocking pin 13b and pushes the unlocking pin 13b to move outward. And when the force transmission pin 14 is located at the lower end surface of the piston sleeve 91, the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c all retract into the inner hole wall of the cylinder 11. The locking pin 13c releases the position limitation on the piston sleeve 91, and the piston sleeve 91 descends normally. At this time, the locking pin 13c abuts against the outer peripheral surface of the piston sleeve 91. The retaining pin 13d is arranged below the locking pin 13c near the lower dead center position of the piston sleeve 91. When the piston sleeve 91 reaches the lower dead center position, its outer peripheral surface contacts the retaining pin 13d, which can ensure that when the piston sleeve 91 leaves its top dead center, at least one of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c abuts against the outer peripheral surface of the piston sleeve 91. See Figure 5 , so as to ensure that they will not reset and protrude into the inner hole of the cylinder 11, avoiding affecting the movement of the piston sleeve 91. Then during the upward stroke, the piston core 92 and the piston sleeve 91 move upward synchronously. When reaching the top dead center, the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c are no longer restricted by the piston sleeve 91 and the unlocking block 15. Under the action of the locking elastic structure, the force transmission plate 13a presses on the piston sleeve 91 again. The retaining pin 13d extends into the inner hole of the cylinder 11 and abuts against the lower end surface of the piston sleeve 91, thereby automatically locking the piston sleeve 91 at the top dead center.

[0209] In this embodiment, the connection between the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c and the force transmission plate 13a can be in the form of a spherical hinge connection or a fixed connection. The unlocking pin 13b, the retaining pin 13d, and the locking pin 13c can be parallel or non-parallel to each other. When they are non-parallel, a spherical hinge connection needs to be adopted to allow deflection during movement. By reasonably setting the connection method and the direction of the holes, it is required that when the force transmission plate 13a moves, it can drive the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c to move smoothly in their respective holes.

[0210] In the cylinder piston device of this embodiment, when the up and down stroke of the piston sleeve 91 is less than the length of the piston sleeve 91, the positions of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c are set so that when the piston sleeve 91 is at its lower dead center, the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c are all located below the upper end surface of the piston sleeve 91. This can effectively prevent the gas in the cylinder 11 from escaping through the holes of the unlocking pin 13b and the locking pin 13c. When the piston sleeve 91 is at its lower dead center and the holes of the unlocking pin 13b and the locking pin 13c are located above the upper end surface of the piston sleeve 91, see Figure 19, that is, it will contact the gas in the cylinder 11. At this time, it is required that the installation and movement of the unlocking pin 13b in the unlocking pin 13b hole, and the installation and movement of the locking pin 13c in the locking pin 13c hole both have good sealing performance, or a closed space is set outside the cylinder 11 to enclose the force transmission plate 13a, unlocking pin 13b, retaining pin 13d, locking pin 13c and other structures of the sleeve locking mechanism 13, ensuring that other parts in the cylinder 11 will not leak from these two holes.

[0211] See Figure 16 , Figure 20 and Figure 21 , in the cylinder piston device of this embodiment, as a preferred design, the sleeve locking mechanism 13 further includes a guiding assembly disposed between the force transmission plate 13a and the cylinder 11. The guiding assembly is used to guide and restrict the linear movement of the force transmission plate 13a. The guiding assembly includes a guiding column 13f. The guiding column 13f is fixedly disposed on the outer wall of the cylinder 11. The guiding column 13f can be fixed on the cylinder 11, or can be fixed on the cylinder supporting structure or other fixed structures around. The axis of the guiding column 13f preferably extends along the radial direction of the cylinder 11. The force transmission plate 13a is provided with a guiding hole and is installed on the guiding column 13f through the guiding hole, moving closer to or away from the cylinder 11 along the guiding column 13f. The guiding column 13f can also be fixedly connected to the force transmission plate 13a. A guiding hole is provided on the outer wall of the cylinder 11 or the supporting structure of the cylinder 11. The guiding column 13f is installed in the guiding hole and can reciprocate along the axis of the guiding hole. The locking elastic structure includes a locking spring 13e. The locking spring 13e is sleeved on the guiding column 13f, and its inner end is connected to or abuts against the force transmission plate 13a. Preferably, an outer wall boss 11a is further provided on the outer wall of the cylinder 11. The force transmission plate 13a is pressed against the outer wall boss 11a, and the two are in surface contact to ensure the stability of the force transmission plate 13a. The unlocking pin through-hole 11f, the retaining pin through-hole 11h and the locking pin through-hole 11g are all provided on the outer wall boss 11a.

[0212] See Figure 16 , Figure 20 and Figure 21 , in the cylinder piston device of this embodiment, the inner hole of the cylinder 11 is of a stepped type, which are the combustion chamber 11d, the first-stage inner hole and the second-stage inner hole from top to bottom in sequence. The combustion chamber 11d can be a spherical segment type. The spherical segment bottom connected to the top end of the first-stage inner hole is the top dead center position of the upper end face of the piston core 92, that is, when the piston core 92 is at the top dead center, the upper part extends out of the piston sleeve 91 and is located in the first-stage inner hole. The piston sleeve 91 moves in the second-stage inner hole. The radius of the first-stage inner hole is smaller than the radius of the second-stage inner hole, and the stepped surface formed between the two constitutes the inter-stage stepped surface 11e. The unlocking pin through-hole 11f, the retaining pin through-hole 11h and the locking pin through-hole 11g are all located in the second-stage inner hole section of the cylinder 11.

[0213] See Figure 22 ,Figure 23 and Figure 24 In the cylinder piston device of this embodiment, the piston sleeve 91 includes a first-stage sleeve section 91b and a second-stage sleeve section 91c connected to the lower end of the first-stage sleeve section 91b. The inner bores of the first-stage sleeve section 91b and the second-stage sleeve section 91c are both cylindrical and coaxial. The inner bore radius of the second-stage sleeve section 91c is greater than that of the first-stage sleeve section 91b, and the stepped surface between the two inner bores forms a second limiting stop surface 91a. The second-stage sleeve section 91c and the second-stage sleeve section 91c can also be connected by a transition surface inclined to the axis, and this transition surface forms the second limiting stop surface 91a. The piston core 92 includes a first-stage core section 92d and a second-stage core section 92e connected to the lower end of the first-stage core section 92d. The first-stage core section 92d and the second-stage core section 92e are also both cylindrical. The outer diameter of the first-stage core section 92d is smaller than that of the second-stage core section 92e, and the stepped surface between the two forms a first limiting stop surface 92a. The first-stage core section 92d and the second-stage core section 92e can also be connected by a transition surface inclined to the axis, and this transition surface forms the first limiting stop surface 92a. The first-stage core section 92d and the second-stage core are respectively located in the first-stage sleeve section 91b and the second-stage sleeve section 91c. An inner piston ring groove 92g is provided on the outer peripheral surface of the first-stage core section 92d for installing an inner piston ring to be in sealing contact with the inner bore of the first-stage sleeve section 91b, and an oil groove is also provided on the outer peripheral surface of the first-stage core section 92d. In this embodiment, the piston core 92 further includes a third-stage core section 92f connected to the lower end of the second-stage core section 92e, and the third-stage core section 92f is connected to the piston rod 10. In addition, the inner bores of the first-stage sleeve section 91b and the second-stage sleeve section 91c can also be non-cylindrical. The cross-sectional area of the inner bore of the first-stage sleeve section 91b is smaller than that of the inner bore of the second-stage sleeve section 91c, and a stepped surface is formed between the two stages, and they can also be connected by a transition surface. Correspondingly, the first-stage core section 92d and the second-stage core section 92e are also both non-cylindrical. The shape of the first-stage core section 92d is adapted to the inner bore of the first-stage sleeve section 91b, and the two are in clearance fit. The shape of the second-stage core section 92e is adapted to the inner bore of the second-stage sleeve section 91c, and the two are in clearance fit. The cross-sectional area of the first-stage core section 92d is smaller than that of the second-stage core section 92e, and a stepped surface is formed between the two stages, and they can also be connected by a transition surface.

[0214] In this embodiment, further, referring to Figure 22 , a hollow inner bore is provided in the second-stage core section 92e, that is, the second-stage core section 92e is a hollow cylindrical structure. The force transmission pin hole 92b is provided on the second-stage core section 92e and penetrates through to the hollow inner bore, that is, it is a radial through hole. The force transmission elastic structure is installed in the hollow inner bore of the second-stage core section 92e and abuts against the inner side end of the force transmission pin 14. The limit of the outward extension of the force transmission pin 14 is independently defined by its outer shape, or by its outer shape and the shape of the channel on the II-stage core section 12e that accommodates the force transmission pin 14, so as to prevent the force transmission pin 14 from falling off outward from the force transmission pin hole 92b.

[0215] In this embodiment, further, referring to Figure 22 , Figure 23 and Figure 24 , the unlocking block 15 is located in the second-stage core section 92e. A strip-shaped through groove extending along the axis is formed in the second-stage sleeve section 91c. The unlocking block 15 is located in the strip-shaped through groove. When the piston core 92 moves relative to the piston sleeve 91, the unlocking block 15 can move in the strip-shaped through groove without collision problems. An outer piston ring is provided on the piston sleeve 91 for sealing contact with the inner wall surface of the inner hole 11j of the cylinder 11. Piston ring grooves are provided on the outer wall of the first-stage sleeve section 91b, and the outer piston ring is installed in these piston ring grooves.

[0216] In this embodiment, further, when the first limiting stop surface 92a of the piston core 92 abuts against the second limiting stop surface 91a of the piston sleeve 91, the upper end surface of the piston core 92 extends out of the upper end surface of the piston sleeve 91. By selecting the extending length, the lower limit of the force on the piston core 92 in the first stage of the power stroke can be controlled. Referring to Figure 7 and Figure 12 . When the force transmission pin 14 on the piston core 92 abuts against the lower end surface of the piston sleeve 91, the upper end surface of the piston sleeve 91 is flush with the upper end surface of the piston core 92, or can also be slightly lower than the upper end surface of the piston core 92. It is also possible to select a configuration in which the upper end surface of the piston core 92 always protrudes above the upper end surface of the piston sleeve 91.

[0217] In this embodiment, further, referring to Figure 14 and Figure 26 , the force transmission release mechanism includes a force transmission pin pressing ring 12. The force transmission pin pressing ring 12 is installed at the lower end of the cylinder 11. An indentation guiding surface is provided on the force transmission pin pressing ring 12 and / or the force transmission pin 14. When the piston core 92 descends to its bottom dead center, the force transmission pin 14 in the extended state will contact the force transmission pin pressing ring 12 through the indentation guiding surface, causing the force transmission pin 14 to be pressed and retracted into the force transmission pin hole 92b. Further, a through hole is provided in the middle of the force transmission locking ring 12 for the piston rod 10 to pass through. Corresponding indentation guiding surfaces are provided on both the force transmission locking ring 12 and the force transmission pin 14 for cooperation. Specifically, the indentation guiding surface on the force transmission locking ring 12 is an upward and inward annular inclined plane 12a provided at the edge of the middle through hole thereof, and the indentation guiding surface on the force transmission pin 14 is a downward and outward inner retracting inclined plane 14a. When the piston core 92 descends to the bottom dead center, the inner retracting inclined plane 14a contacts the annular inclined plane 12a, thereby pressing the force transmission pin 14 to move inward. In this embodiment, preferably, there are multiple force transmission pins 14, which are evenly arranged circumferentially, and all the force transmission pins 14 contact the annular inclined plane 12a synchronously.

[0218] The present invention also provides an operating method for a piston engine, which is used for the operation of a piston engine including the above-mentioned power equipment, and also includes existing structures such as an intake valve, an exhaust valve, and an ignition device when necessary. A combustion chamber 11d is provided at the top inside the cylinder 11. An intake hole 11b, an exhaust hole 11c, and a spark plug hole are also provided at the top of the cylinder 11, which are respectively used for installing the intake valve, the exhaust valve, and the activation spark plug. For the convenience of description, the angle corresponding to the crank 1 when the passive slider 4 is at its lower limit position is called the bottom dead center angle. At this time, the crank 1 and the connecting rod 2 are collinear and in opposite directions, and the outer end (the end not connected to the crank) of the connecting rod is closest to the crank axis. See Figure 27 as shown. In the piston engine, preferably, the rotation center of the crank 1 is eccentrically arranged. The eccentric arrangement means that there is a certain eccentric distance h between the rotation center of the crank 1 and the axis of the piston 9. This eccentric arrangement is beneficial to better convert the force of the piston 9 into the torque for driving the crank 1. With this deviation design, when the crank 1 is at the zero-degree phase angle 0°, see Figure 30 , an angle α0 will be formed between the crank 1 and the axis of the piston 9. Of course, the rotation center of the crank 1 can also be located on the axis of the piston 9 without eccentric arrangement, and at this time α0 = 0. For the above two eccentric and non-eccentric arrangement methods, the operating principle of the piston engine is basically the same. For the convenience of description, in the description of the operating method, the rotation angle of the crank 1 is referenced with its zero-degree phase angle 0° as the reference, rather than the axis of the piston 9 as the reference. The crank 1 rotates continuously in a cycle in the manner shown in the appendix Figure 41 .

[0219] The operating method of the piston engine includes the following processes:

[0220] A1. Exhaust stroke process: The exhaust valve opens, the crank 1 rotates from the bottom dead center angle towards the transmission disconnection angle, the clutch mechanism 6 maintains the transmission connection state, the piston rod 10 moves upward from its lower dead center, the piston 9 discharges the waste gas in the cylinder 11. When the crank 1 reaches the transmission disconnection angle, the piston rod 10 reaches its upper dead center, and the position holding mechanism 7 locks the position of the piston rod 10, and the clutch mechanism 6 switches to the transmission disconnection state.

[0221] When the piston engine in this embodiment is adopted, specifically, for the exhaust stroke process, see Figures 27 to 28The process shown is as follows. At the start of this stroke, the exhaust valve opens, the crank 1 is at the bottom dead center angular position, the passive slider 4 is at its lower limit position, the piston rod 10 is at the bottom dead center. At the same time, in the cylinder piston device, the force - transmitting pin 14 also retracts into the outer peripheral surface of the piston core 92. During the subsequent upward movement, the piston core 92 can smoothly move upward relative to the piston sleeve 91 to the position where the first limit stop surface abuts against the second limit stop surface, thereby driving the piston sleeve 91 to move upward together. And the wedge 709 in the position - holding mechanism changes from the extended state to the retracted state to avoid collision with other components during the subsequent upward movement. Since the clutch mechanism 6 remains in the transmission - connected state, when the crank 1 rotates counterclockwise in the direction shown in the figure, through the connecting rod 2, the passive slider 4, the clutch mechanism 6 and the sliding actuator 5, the piston rod 10 is driven to move upward. At this time, the position - holding mechanism 7 is in the unlocked state, and the wedge 709 therein is in the retracted state, which does not affect the movement of the piston 9. When the crank 1 approaches the transmission - disconnection angle and the piston rod 10 approaches its top dead center, the clutch mechanism 6 starts the switching process to the connection - disconnection state (the specific process is referred to above and will not be elaborated here). At the same time, the position - holding mechanism 7 undergoes a reset - locking process (the specific process is referred to above and will not be elaborated here). When the crank 1 reaches the transmission - disconnection angle, the piston rod 10 reaches its top dead center, and both the piston core 92 of the piston 9 and the piston sleeve 91 reach their top dead centers. The position - holding mechanism 7 completes the reset - locking and locks the position of the piston rod 10. Refer to Figure 29 , the piston 9 is locked and cannot move downward, and the clutch mechanism 6 also completes the switching and is in the transmission - disconnection state. The transmission connection between the connecting rod 2 and the piston rod 10 is disconnected. At the same time, in the cylinder piston device, the piston sleeve 91 is also locked at its top dead center by the sleeve locking mechanism 13, and the exhaust process ends.

[0222] A2. Intake waiting process: The clutch mechanism 6 remains in the transmission - disconnection state. The crank 1 rotates from the transmission - disconnection angle to the zero - phase - angle and then to the transmission - connection angle. The piston rod 10 remains at its top dead center. When the crank 1 reaches the transmission - connection angle, it switches to the transmission - connected state. The exhaust valve closes and the intake valve opens.

[0223] When the piston - type engine in this embodiment is adopted, specifically, for the intake waiting process, refer to Figures 28 to 30 Then to Figure 32 the process shown. During the whole process, both the piston rod 10 and the piston 9 remain stationary, and the volume of the closed space formed by the top of the piston 9 and the cylinder 11 remains unchanged. When the crank 1 rotates to the 0° phase - angle, the passive slider reaches its top dead center, and the wedge 709 in the position - holding mechanism changes from the retracted state to the extended state, preparing for unlocking the position - holding mechanism during the subsequent downward movement. After the crank 1 rotates past the 0° phase - angle, the passive slider starts to move downward. When the crank 1 approaches the transmission - connection angle, the clutch mechanism 6 starts the switching process to the transmission - connected state (the specific process is referred to above and will not be elaborated here). Refer to Figure 33As shown, the position holding mechanism 7 is undergoing an unlocking process (for the specific process, refer to the above text and details will not be repeated here). When the crank 1 reaches the transmission connection angle, the clutch mechanism 6 completes the switching and changes to the transmission connection state. The transmission connection between the connecting rod 2 and the piston rod 10 is re-established. The position holding mechanism 7 completes the unlocking, and the piston rod 10 is unlocked, getting ready for the downward movement. The opening of the intake valve and the closing of the exhaust valve can be selected at any moment during this process.

[0224] A3. Intake stroke process: The crank 1 rotates from the transmission connection angle towards the bottom dead center angle. The clutch mechanism 6 maintains the transmission connection state. The piston 9 moves downward. When the crank 1 reaches the bottom dead center angle, the piston rod 10 reaches its bottom dead point, and the intake valve closes.

[0225] When adopting the piston engine in this embodiment, specifically, for the intake stroke process, refer to Figures 32 to 34 and then to Figure 35 the process shown. At the beginning, the exhaust valve is already closed and the intake valve is already open. The crank 1 continues to rotate, driving the piston rod 10 to move downward through the connecting rod 2, the passive slider 4, the clutch mechanism 6, and the sliding actuator 5. At this time, the position holding mechanism 7 is in the unlocked state and does not affect the movement of structures such as the piston 9. When the crank 1 reaches the bottom dead center angle, the passive slider 4 reaches its lower limit position, and the piston rod 10 reaches its bottom dead point. At this time, both the piston core 92 and the piston sleeve 91 of the piston 9 also reach their bottom dead points. At the same time, in the cylinder piston device, the force transmission pin 14 also retracts into the outer peripheral surface of the piston core 92. When moving upward later, the piston core 92 can smoothly move upward relative to the piston sleeve 91 to the position where the first limit surface abuts against the second limit surface, thereby driving the piston sleeve to move upward together.

[0226] A4. Compression stroke process: The crank 1 rotates from the bottom dead center angle towards the transmission disconnection angle. The clutch mechanism 6 maintains the transmission connection state. The piston rod 10 moves upward, and the piston 9 compresses the gas in the cylinder 11. When the crank 1 reaches the transmission disconnection angle, the piston rod 10 reaches its top dead point, and the position holding mechanism 7 locks the position of the piston rod 10, and the clutch mechanism 6 switches to the transmission disconnection state.

[0227] When adopting the piston engine in this embodiment, specifically, for the compression stroke process, that is Figures 35 to 36 the process shown. The movement processes of the components in this process are the same as those of the same components in the exhaust stroke process, so the specific process will not be repeated here. At the end of the compression stroke process, the gas in the cylinder 11 is compressed to have a very high pressure, waiting to be ignited or have oil mist injected and then explode.

[0228] A5. Ignition and Combustion Delay Process: The crank 1 rotates from the transmission disconnection angle to the zero phase angle and then to the transmission connection angle. The piston rod 10 remains at its top dead center. Ignition or fuel injection can start at any moment during this period. When the crank 1 reaches the transmission connection angle, it switches to the transmission connection state.

[0229] When adopting the piston engine in this embodiment, specifically, the ignition and combustion delay process can also be called the pre-power stroke process. Refer to Figures 36 to 37 Then to Figure 38 the process shown. During this process, the movement processes of each component are the same as those of the same components in the above intake waiting process. Therefore, the specific process will not be elaborated here. Ignition or fuel injection can be selected to start at any moment during this process. Preferably, the ignition start moment is selected in the interval when the crank 1 rotates from the zero phase angle to the transmission connection angle. The time period before ignition during this interval is called the ignition waiting time period, and the process experienced by the engine during this time period is called the ignition waiting process. The time period after ignition is the combustion delay time period, and the process experienced is called the combustion delay process. When this process ends, the fuel in the combustion chamber has almost reached or reached complete combustion, forming ideal high-pressure gas.

[0230] A6. Power Stroke Process: The clutch mechanism 6 remains in the transmission connection state. The high-pressure gas in the cylinder 11 drives the piston 9 to move downward. The piston rod 10 drives the crank 1 to rotate from the transmission connection angle to the bottom dead center angle, and the piston rod 10 reaches its bottom dead center.

[0231] When adopting the piston engine in this embodiment, specifically, the power stroke process, that is Figures 38 to 39 Then to Figure 10 the process shown. The high-pressure gas in the cylinder 11 drives the piston 9 to move downward. Specifically, the piston core 92 of the piston 9 moves downward first. Refer to Figure 39 shown. When the force transmission pin extends out and abuts against the lower edge of the piston sleeve, the piston sleeve 91 is unlocked and then moves downward synchronously with the piston core 92. The specific process and principle are as described above and will not be elaborated here. When the piston rod 10 moves downward with the piston 9, it drives the connecting rod 2 to move through the intermediate mechanism composed of the sliding actuator 5, the clutch mechanism 6, and the passive slider 4. The connecting rod 2 drives the crank 1 to rotate. During this process, the position maintaining mechanism 7 is in the unlocked state and does not affect the movement of structures such as the piston 9. When the crank 1 reaches the bottom dead center angle, the passive slider 4 reaches its lower limit position, and the piston rod 10 reaches its bottom dead center. At this time, the piston core 92 and the piston sleeve 91 of the piston 9 also reach their bottom dead centers. At the same time, in the cylinder piston device, the force transmission pin 14 also retracts into the outer peripheral surface of the piston core 92 so that it can smoothly enter the piston sleeve 91 during the subsequent upward movement.

[0232] When the piston engine completes the processes from A1 to A6, it has completed a full cycle of work, and then cyclically performs the processes from A1 to A6 to continuously work and output power through the crank 1 shaft.

[0233] For the piston engine of the present invention, during operation, compared with the existing traditional design, an intake waiting process and a waiting ignition and combustion delay process are added. When the high-pressure gas starts to push the piston 9 to do work, the crank 1 has rotated a certain angle from the zero-degree phase angle to reach the transmission connection angle θ2. At this time, the connecting rod 2 and the crank 1 have passed the collinear position, and the center line of the connecting rod is significantly deviated from the rotation center of the crank 1, providing a sufficiently long lever arm for the driving force. Refer to Figure 38 As shown, the size of the transmission connection angle θ2 can be set according to the actual situation and should be as close as possible to the preferred transmission range (generally about 40°).

[0234] Cylinder piston device embodiment two:

[0235] The inner hole 11j of the sleeve and the piston sleeve 91 in the cylinder piston device of the present invention can also be of the second level or above. Refer to Figures 42 to 44 In the cylinder piston device embodiment two shown, the cylinder 11 is provided with an inner core hole 11i and an N-level inner hole 11j from top to bottom in sequence, and the number of levels N = 2. The cross-sections of the inner core hole 11i to the N-level inner hole 11j increase in sequence, that is, the cross-section of the first-level inner hole 11j is larger than that of the inner core hole 11i. In this way, an inter-level stepped surface 11e is formed between the inner core hole 11i and the first-level inner hole 11j. The cross-section of the second-level inner hole 11j is larger than that of the first-level inner hole 11j, and an inter-level stepped surface 11e is also formed between them. The piston 9 includes a piston core 92 and an N-level piston sleeve 91 from inside to outside in sequence, and the number of levels N = 2. The first-level piston sleeve 91 located inside is sleeved on the piston core 92 and can move up and down relatively. The second-level piston sleeve 91 located outside is sleeved on the first-level piston sleeve 91 and can move up and down relatively. The second-level piston sleeve 91 is located in the second-level inner hole 11j and moves up and down in it.

[0236] For the cylinder piston device of this embodiment, compared with the single-level inner hole 11j and piston sleeve 91 in embodiment one, the second-level inner hole 11j and the second-level piston sleeve 91 are added. Correspondingly, a force transmission mechanism is added between adjacent two-level piston sleeves 91, and a sleeve locking mechanism 13 is added to realize the locking function of the second-level piston sleeve 91. Among them, the structure and action principle between the first-level piston sleeve 91 and the piston core 92 are basically the same, so they will not be described in detail here, and reference can be made to embodiment one.

[0237] In this embodiment, the second-stage piston sleeve 91 is located in the inner hole 11j of the second stage and moves up and down therein. The first-stage and second-stage piston sleeves are respectively provided with a third limit stop surface and a fourth limit stop surface, and the first-stage piston sleeve 91 can move upward relative to the second-stage piston sleeve 91 until the third limit stop surface and the fourth limit stop surface are in contact. When the piston core 92 is at its top dead center, the upper end of the piston core 92 is located in the inner hole 11i of the core. The upper end of the first-stage piston sleeve 91 extends into the inner hole 11j of the first stage and is close to the stage step surface 11e at the upper end of the inner hole 11j of the first stage. At this time, the third limit stop surface and the fourth limit stop surface of the two-stage piston sleeves 91 are in contact.

[0238] In this embodiment, a force transmission mechanism is also provided on the first-stage piston sleeve 91 for transmitting force to the second-stage piston sleeve 91. The structure and function of this force transmission mechanism are the same as those of the force transmission mechanism on the piston core 92. A force transmission pin hole is also provided on the outer side surface of the first-stage piston sleeve 91, and the force transmission pin 14 of the force transmission mechanism is installed in this force transmission pin hole. When the third limit stop surface on the first-stage piston sleeve 91 is in contact with the fourth limit stop surface on the first-stage piston sleeve 91, the force transmission pin 14 on the inner first-stage piston sleeve 91 is located above the lower end surface of the outer piston sleeve 91, and thus will partially or completely enter the inner cavity of the outer piston sleeve 91.

[0239] In this embodiment, when the piston core 92 reaches the top dead center, the positions of both the two-stage piston sleeves 91 can be locked by the sleeve locking mechanism 13. The sleeve locking mechanism 13 adopts the same structure as that in the first embodiment, and the number is two, which are respectively used to lock the N-stage piston sleeves 91. That is, on the basis of the first embodiment, an additional sleeve locking mechanism 6 is added to lock the second-stage piston sleeve 91. The working principles of locking and unlocking of the two sleeve locking mechanisms 13 are basically the same. Specifically, when the second-stage piston sleeve 91 reaches its top dead center, the locking pin 13c of the sleeve locking mechanism 13 for locking the second-stage piston sleeve 91 abuts against the lower end face of the second-stage piston sleeve 91, thereby locking the position of the second-stage piston sleeve 91 and preventing it from moving downward. At this time, the upper end face of the second-stage piston sleeve 91 may be flush with or not flush with the upper end face of the first-stage piston sleeve 91. The release of the sleeve locking mechanism 13 for locking the second-stage piston sleeve 91 is achieved by the first-stage piston sleeve 91, and the principle is basically the same as that of the piston core 92 releasing the sleeve locking mechanism 13 for locking the first-stage piston sleeve 91. Specifically, an unlocking block 15 is also fixedly provided on the first-stage piston sleeve 91, and an unlocking inclined surface 15a is provided on the lower side of the unlocking block 15. When the first-stage piston sleeve 91 moves downward from its top dead center, the unlocking inclined surface 15a of the unlocking block 15 thereon can contact the unlocking pin 13b of the sleeve locking mechanism 13 for locking the second-stage piston sleeve 91 and drive the unlocking pin 13b to move outward until it retracts into the inner hole wall of the cylinder 11, thereby releasing the locking of the second-stage piston sleeve 91 and enabling the second-stage piston sleeve 91 to move downward smoothly. Moreover, when the second-stage piston sleeve 91 leaves its top dead center, at least one of the unlocking pin 13b, the retaining pin 13d, and the locking pin 13c of its corresponding sleeve locking mechanism 13 also abuts against the outer peripheral surface of the second-stage piston sleeve 91 to ensure that the sleeve locking mechanism 13 remains in the unlocked state.

[0240] In this embodiment, when the piston core 92 reaches the bottom dead center, the force transmission release mechanism will also contact the force transmission pin 14 in the extended state on the first-stage piston sleeve 91 and compress the force transmission pin 14 into the force transmission pin hole, so that the second-stage piston sleeve 91 can move downward relative to the first-stage piston sleeve 91 to the bottom dead center.

[0241] During the operation of the cylinder piston device in this embodiment, the working process and principle of the piston core 92 of the piston 9 and the first-stage piston sleeve 91 are the same as those in the first embodiment. The difference is that there is an additional operation process of the second-stage piston sleeve 91. Similarly, taking the application in an engine as an example, when the cylinder piston device in this embodiment operates cyclically, the following processes are carried out in sequence:

[0242] (a) During the compression stroke process, when the piston core 92 and the two-stage piston sleeve 91 are both at their bottom dead centers, the force transmission pin 14 on the piston core 92 retracts into the force transmission pin hole 92b under the action of the force transmission release mechanism. At the same time, the force transmission pin 14 on the first-stage piston sleeve 91 also retracts into the force transmission pin hole under the action of the force transmission release mechanism. The piston rod 10 drives the piston core 92 to move upward, and the force transmission pin 14 thereon can smoothly enter the first-stage piston sleeve 91. Since the upper end faces of the two-stage piston sleeve 91 are both subjected to gas pressure, the piston core 92 will move upward until the first limit stop surface 92a abuts against the second limit stop surface 91a of the first-stage piston sleeve 91. The piston core 92 drives the first-stage piston sleeve 91 to move upward synchronously through the pressure between the first limit stop surface 92a and the second limit stop surface 91a. Then, the first-stage piston sleeve 91 moves upward until the third limit stop surface abuts against the fourth limit stop surface of the second-stage piston sleeve 91, driving the second-stage piston sleeve 91 to move upward synchronously, and the entire piston 9 moves upward synchronously. When the piston core 92 reaches its top dead center, the upper part is located in the core inner hole 11i. The first-stage piston sleeve 91 reaches its top dead center, and its upper end extends into the first-stage sleeve inner hole 11j, and its upper end face is close to or abuts against the inter-stage step surface 11e at the upper end of the first-stage sleeve inner hole 11j. The corresponding sleeve locking mechanism 13 locks the first-stage piston sleeve 91 at its top dead center. At the same time, the second-stage piston sleeve 91 reaches its top dead center, and its upper end face is close to or abuts against the inter-stage step surface 11e at the upper end of the second-stage sleeve inner hole 11j. The corresponding sleeve locking mechanism 13 locks the second-stage piston sleeve 91 at its top dead center.

[0243] (b) During the power stroke, both of the two-stage piston sleeves 91 remain stationary first. Under the action of the high-pressure combustion gas, the piston core 92 moves downward first. When the force-transfer pin 14 on the piston core 92 reaches the lower end face of the first-stage piston sleeve 91, the force-transfer pin 14 extends out of the outer peripheral surface of the piston core 92 under the action of the force-transfer elastic structure. At the same time, the sleeve locking mechanism 13 releases the locking of the first-stage piston sleeve 91. The combustion gas acts on the upper end face of the first-stage piston sleeve 91, and the formed pressure pushes the first-stage piston sleeve 91 downward. And this pressure is preferably greater than the pressure acting on the piston core 92. When the first-stage piston sleeve 91 moves downward, its lower end face will push the force-transfer pin 14, so as to move downward synchronously with the piston core 92. At the same time, when the force-transfer pin 14 on the first-stage piston sleeve 91 reaches the lower end face of the second-stage piston sleeve 91, the force-transfer pin 14 extends out of the outer peripheral surface of the piston core 92 under the action of the force-transfer elastic structure. At the same time, the sleeve locking mechanism 13 releases the locking of the second-stage piston sleeve 91. The combustion gas acts on the upper end face of the second-stage piston sleeve 91, and the formed pressure pushes the second-stage piston sleeve 91 downward. And this pressure is preferably greater than the pressure acting on the first-stage piston sleeve 91. When the second-stage piston sleeve 91 moves downward, its lower end face will push the force-transfer pin 14 on the first-stage piston sleeve 91, so as to move downward synchronously with the first-stage piston sleeve 91. In this way, the whole piston 9 moves downward synchronously. During the process that the piston core 92 approaches the bottom dead center and reaches its bottom dead center, the force-transfer pin 14 on the piston core 92 retracts into the force-transfer pin hole 92b under the action of the force-transfer release mechanism and does not extend out of the outer peripheral surface of the piston core 92. The first-stage piston sleeve 91 can reach its bottom dead center synchronously with the piston core 92 or can reach it out of sync. At this time, the first-stage piston sleeve 91 will continue to move downward under the action of the combustion gas pressure and then reach its bottom dead center. At the same time, the force-transfer pin 14 on the second-stage piston sleeve 91 will also retract under the action of the force-transfer release mechanism. The second-stage piston sleeve 91 can reach its bottom dead center synchronously with the first-stage piston sleeve 91 or can reach it out of sync. At this time, the second-stage piston sleeve 91 will continue to move downward under the action of the combustion gas pressure and then reach its bottom dead center.

[0244] (c) During the exhaust stroke, the piston rod 10 drives the piston core 92 to move upward. The piston core 92 will push the first-stage piston sleeve 91 to move upward together through the pressure between the first limiting surface 92a and the second limiting surface 91a. The first-stage piston sleeve 91 will push the second-stage piston sleeve 91 to move upward together through the pressure between the third limiting surface and the fourth limiting surface. The piston 9 can move upward synchronously as a whole. Then the piston core 92 reaches its top dead center, and the two-stage piston sleeves 91 also reach their top dead centers. Their upper end faces abut against or are close to the corresponding step surfaces 11e between stages. The corresponding sleeve locking mechanisms 13 lock the two-stage piston sleeves 91 at their top dead centers respectively.

[0245] (d) Intake stroke process, which is the same as the above power stroke process, except that the uncompressed gas in the cylinder pushes the piston 9 downward, so the specific process will not be elaborated here.

[0246] Therefore, when the cylinder piston device in this embodiment is adopted, during the power stroke, it is divided into three stages. In the first stage, the two-stage piston sleeve 91 remains stationary while the piston core 92 moves first. In the second stage, the first-stage piston sleeve 91 and the piston core 92 move downward synchronously, while the second-stage piston sleeve 91... Therefore, when the gas pressure is the highest, the force is transmitted only through a part of the cross-section of the piston 9 (the cross-section part of the piston core 92) and is transmitted through the piston rod 10, and finally transmitted to the crank. Then, in the third stage, the second-stage piston sleeve 91, the first-stage piston sleeve 91, and the piston core 92 move downward synchronously.

[0247] In the cylinder piston device of the present invention, in other embodiments, more levels of inner holes 11j and piston sleeves 91 can be added according to actual situations, that is, the number of levels N can be 3 or more. Correspondingly, a force transmission mechanism is added between adjacent two-stage piston sleeves 91, and a sleeve locking mechanism 13 is correspondingly added to lock each stage of piston sleeve 91 respectively. In the case of adding more levels of inner holes 11j and piston sleeves 91, its structure and working principle are the same as those when the second-level inner hole 11j and piston sleeve 91 are added in the second embodiment, so it will not be elaborated one by one.

[0248] As can be seen from the above, the crank connecting rod motion device, power equipment, and piston engine operation method of the present invention have the following beneficial effects:

[0249] 1. The piston 9 can be kept at the top dead center when the gas starts to burn, and the combustion is carried out under constant volume conditions to obtain a higher peak pressure. When the gas in the cylinder 11 reaches the peak pressure, the phase angle of the crank 1 has turned to a position far enough after passing through zero, so that the force arm of the force transmitted to the crank 1 through the connecting rod 2 with respect to the rotation center of the crank 1 is long enough at this time, thereby effectively converting the driving force generated by the peak pressure into a torque that matches the value to drive the crankshaft to rotate. Such an improvement can not only significantly increase the maximum torque of the engine, but also significantly increase the average torque of the engine, which is beneficial to increasing the power of the engine. And when the combustion occurs, the piston 9 is already at the top dead center, and no additional work is required to compress the partially burned mixed gas, so the efficiency of the engine will also be significantly improved.

[0250] 2. By setting up the piston 9 composed of the piston core 92 and the piston sleeve 91, at the initial stage of the power stroke when the gas pressure is extremely high, the force-bearing surface of the piston 9 under the action of the gas is reduced, avoiding excessive impact loads on the crankshaft and making the gas driving force acting on the piston 9 more evenly converted into torque. Moreover, the increased volume of the gas after expansion in this initial stage is only the volume of the I-level inner diameter section of the cylinder. The angle turned by the crank 1 corresponds to the moving distance of the piston rod here, that is, the piston core. Thus, with a smaller expansion of the gas volume (pressure attenuation), the same crank angle is obtained, enabling the gas in the same state to have higher working capacity within a larger crank angle range.

[0251] 3. It can create conditions for reducing the size of the main force-transmitting components, reducing the weight of the structure, and improving the control accuracy of the ignition time, etc.

[0252] 4. It is beneficial to improve the specific torque and specific power of the engine: Under the conditions of the same intake air volume, compression ratio, air-fuel mixture ratio, rotational speed, and peak pressure, by increasing the radius of the crank 1 and reducing the diameter of the cylinder 11, when the maximum thrust acting on the piston 9 is significantly reduced, the torque and power of the engine can still be significantly increased synchronously. The reduction of the maximum thrust on the piston 9 is beneficial to reducing the size of relevant components under the same strength conditions, thereby reducing the weight of the engine. Or, with the diameter of the cylinder 11 unchanged, by appropriately adjusting the length of the crank 1 and the eccentricity h between the rotation center of the crank 1 and the axis of the piston 9, the torque and power of the engine can also be significantly increased under the same thrust of the cylinder 11. Both of these two ways can achieve the effect of improving the torque and power per unit weight of the engine.

[0253] 5. It can simultaneously improve the torque, power, and efficiency of the engine: First, since the piston and the connecting rod are not directly connected, a longer crank can be selected without the connecting rod hitting the cylinder wall, thus effectively increasing the piston stroke to increase the intake air volume. Under the condition that the fuel flow rate and the volume of the combustion chamber 11d are the same as those of the traditional engine system, although the air-fuel mixture concentration decreases, the compression ratio increases, and the initial pressure of the mixed gas increases, and finally a higher peak pressure can be obtained; Second, by using the piston 9 composed of the piston core 92 and the piston sleeve 91 and matching with a cylinder with a stepped inner hole, the peak pressure first acts on the piston core 92 part with a smaller cross-section. After the piston core 92 moves a certain distance, the pressure decreases, and then the gas acts on both the piston core and the piston sleeve 91 part with a larger cross-section at the same time, so as to control the driving force and torque within a lower and more ideal range while ensuring sufficient torque all the time, avoiding excessive impact loads; Moreover, since the piston rod 10 is not directly connected to the connecting rod 2, a sufficiently large eccentricity can be selected to obtain as large a lever arm length as possible during the power stroke, so as to obtain as large a torque as possible through the piston 9 with a small cross-section.

[0254] 6. It can reduce the power loss caused by sliding friction resistance. Among the friction losses of existing internal combustion engines, 60% is caused by the friction between the piston 9 and the cylinder 11. The most direct reason is the lateral force exerted on the piston 9 by the connecting rod 2. In the engine of the present invention, the piston rod 10 is separated from the connecting rod 2, and the lateral force caused by the reaction force of the connecting rod 2 no longer directly acts on the piston 9. In addition, when an eccentric design is adopted, the angle between the axis of the connecting rod and the piston is very small when the piston is driven by the combustion gas, thereby significantly reducing the friction force between the cylinder 11 and the piston 9. Even if the eccentric design is not adopted, the lateral force can be controlled within a reasonable range by selecting the geometric parameters and materials of the components. Although the force of the connecting rod 2 will generate a lateral force on the passive slider 4, most of the lateral force is transmitted to the fixed support 701 through the sliding actuator 5 and the position holding mechanism 7. Due to the differences in materials and working environments, the friction coefficient between the passive slider 4, the sliding actuator 5 and the position holding mechanism 7 can be much smaller than the friction coefficient between the cylinder 11 and the piston 9. In addition, the reduction of the driving force on the piston 9 caused by the adoption of the sleeve piston 9 will reduce the reaction force of the connecting rod 2. Moreover, appropriately increasing the eccentricity h of the crank rotation center and the length ratio of the crank 1 of the connecting rod 2 can make the angle between the axis of the connecting rod 2 and the guiding piston 9 smaller during the power stroke. The superposition of these many favorable factors will more significantly reduce the energy loss caused by sliding friction.

[0255] 7. It is beneficial to improve the structure of the piston engine and avoid other moving components except the piston 9 and the piston 9 ring from contacting the high-temperature combustion gas, especially preventing the combustion gas from leaking into the crankcase side and polluting or even burning the lubricating oil. In the case of the direct connection of the piston 9 - connecting rod 2 - crankshaft in the traditional piston 9 engine, due to the swing of the connecting rod 2, it is difficult to separate and seal the cylinder 11 and the crankcase. In the present invention, a seal can be selected to be provided at or near the position of the force-transmitting pin pressing ring 12 on the side of the V-shaped connecting block 802, separating the cylinder 11 from components such as the sliding actuator 5, the connecting rod 2 and the crankshaft.

[0256] 8. Due to the intake waiting process, the control requirements for the intake and exhaust time points are reduced, which is beneficial to changing the valve control method from cam pushrod control to control by the position of a linear motion component directly related to the movement of the piston 9, simplifying the control mechanism and improving the control accuracy.

[0257] In summary, the present invention effectively overcomes various shortcomings in the prior art and has high industrial utilization value.

[0258] The above embodiments are only illustrative of the principles and effects of the present invention and are not intended to limit the present invention. Any person familiar with this technology can modify or change the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or changes made by those with ordinary knowledge in the relevant technical field without departing from the spirit and technical idea disclosed by the present invention should still be covered by the claims of the present invention.

Claims

1. A crank - connecting rod motion device, comprising a crank (1), a connecting rod (2) and a linear sliding member (3). One end of the connecting rod (2) is hinged to the crank (1). The linear sliding member (3) moves linearly in the up - and - down direction, and the linear sliding member (3) is located above the crank (1), and is characterized in that: It further includes a passive slider (4), a sliding actuator (5), a clutch mechanism (6) and a position holding mechanism (7). The sliding actuator (5) is connected to the linear slider (3) and the two move linearly synchronously. The passive slider (4) is hinged to the other end of the connecting rod (2). The clutch mechanism (6) is arranged between the passive slider (4) and the sliding actuator (5), and the clutch mechanism (6) has a transmission connection state and a transmission disconnection state. When the clutch mechanism (6) is in the transmission connection state, the passive slider (4) establishes a motion connection with the sliding actuator (5) and moves up and down synchronously. When the clutch mechanism (6) is in the transmission disconnection state, the passive slider (4) disconnects the motion connection with the sliding actuator (5), and the passive slider (4) can move linearly up and down relative to the linear slider (3). When the passive slider (4) reaches the upper limit position, the phase angle corresponding to the crank (1) is the zero phase angle, and a transmission disconnection angle and a transmission connection angle are respectively provided before and after the zero phase angle along the rotation direction. When the crank (1) rotates from the transmission disconnection angle to the transmission connection angle, the passive slider (4) first moves upward to the upper limit position and then moves downward away from the upper limit position. During the process of the crank (1) rotating from the transmission connection angle to the transmission disconnection angle, the clutch mechanism (6) is in the transmission connection state. During the process of the crank (1) rotating from the transmission disconnection angle to the transmission connection angle, the clutch mechanism (6) is in the transmission disconnection state, and the linear slider (3) is located at its upper limit position. When the crank (1) is at the transmission connection angle and the transmission disconnection angle, the clutch mechanism (6) completes the state switching. When the crank (1) reaches the transmission disconnection angle, the position holding mechanism (7) is triggered to act and can lock the position of the linear slider (3). When the crank (1) reaches the transmission connection angle, the position holding mechanism (7) is triggered to act and releases the position locking of the linear slider (3).

2. The crank - connecting rod motion device according to claim 1, characterized in that: A driving boss (401) is fixedly arranged on the passive slider (4). The sliding actuator (5) includes a driving block (501), a driving bolt (502) and a first return spring (503). The driving block (501) moves linearly in the up and down direction and is directly or indirectly connected to the linear sliding member (3). One end of the driving bolt (502) is hinged to the driving block (501), and the other end is a swinging end. The driving bolt (502) is located above the driving boss (401). The first return spring (503) is installed on the driving block (501) and acts on the driving bolt (502). The first return spring (503) applies an elastic force to the driving bolt (502) to drive the driving bolt (502) to swing downward until the swinging end abuts against the driving boss (401). The clutch mechanism (6) includes a top block (601), a locking block (603), a second return spring (602), a third return spring (604), an action execution component, and a trigger component. The top block (601), the locking block (603), the second return spring (602), the third return spring (604) and the action execution component are all installed on the passive slider (4). The top block (601) is located above the driving boss (401) and on one side of the swinging end of the driving bolt (502). The top block (601) can linearly move relative to the passive slider (4) to approach or move away from the swinging end of the driving bolt (502). The second return spring (602) acts on the top block (601) and provides an elastic force to drive the top block (601) to abut against the swinging end of the driving bolt (502). The locking block (603) can linearly move up and down relative to the passive slider (4), and when the locking block (603) moves, it can enter or leave the side of the top block (601) away from the driving bolt (502) through a guiding surface. The third return spring (604) acts on the locking block (603) and provides an elastic force to drive the locking block (603) to enter the side of the top block (601) away from the driving bolt (502) and abut against it. The action execution mechanism is connected to the locking block (603). The trigger component cannot translate in the left and right directions. During the crank (1) rotates from the transmission connection angle to the transmission disconnection angle, the locking block (603) abuts against the top block (601), and the swinging ends of the driving bolts (502) respectively abut against the top block (601) and the driving boss (401). When the crank (1) rotates to the transmission disconnection angle, the action execution component contacts and acts on the trigger component and drives the locking block (603) away from the top block (601). When the crank (1) rotates to the transmission connection angle, the action execution component is separated from the trigger component, and the locking block (603) resets to the side of the top block (601) away from the driving bolt (502) and abuts against it.

3. The crank-link motion device according to claim 2, characterized in that: The action execution mechanism includes an action execution swing arm (606) and an action execution connecting rod (605). The middle of the action execution swing arm (606) is hinged to the passive slider (4), one end thereof is a trigger action end, and the other end is hinged to one end of the action execution connecting rod (605). The other end of the action execution connecting rod (605) is hinged to the locking block (603). The trigger assembly includes an action claw (607) and a fixed limit rod (608) located above the action claw (607). The fixed limit rod (608) extends in the up and down direction. A downward trigger slope (607a) is provided on the action claw (607). When the passive slider (4) moves from the lower limit position to the upper limit position, the trigger action end of the action execution swing arm (606) can contact the trigger slope (607a) and then abut against the fixed limit rod (608). When the trigger action end of the action execution swing arm (606) moves along the trigger slope (607a), the action execution swing arm (606) rotates and drives the locking block (603) away from the top block (601) through the action execution connecting rod (605). When the trigger action end abuts against the fixed limit rod (608), the locking block (603) remains in the separated state.

4. The crank and connecting rod motion device according to claim 3, characterized in that: The action claw (607) is rotatably installed. An upward relaxation surface (607b) is provided on the action claw (607). The trigger assembly further includes a fourth return spring (609). The fourth return spring (609) acts on the action claw (607) and provides an elastic force to urge the action claw (607) to abut against the lower side end of the fixed limit rod (608). When the passive slider (4) moves from the upper limit position to the lower limit position, the trigger action end of the action execution swing arm (606) abuts against the relaxation surface (607b) of the action claw (607), forcing the action claw (607) to rotate and swing downward, and the execution swing arm (606) can smoothly rotate until the locking block (603) enters the side of the top block (601) away from the driving bolt (502).

5. The crank connecting rod motion device according to claim 2, characterized in that: The driving block (501) of the sliding actuator (5) is provided with a downward locking inclined surface (501a) and a transition surface (501c) connected to the upper side of the locking inclined surface (501a); the position holding mechanism (7) includes a fixed support (701), a latch (703), a latch block (705), a lever (706), a push arm (708), a fifth return spring (704), a sixth return spring (707), a holding support plate (722), a wedge block assembly, and an extending trigger structure. The latch (703) is rotatably mounted on the fixed support (701) and is provided with a top-holding portion and a rotation-blocking portion. The fifth return spring (704) is arranged between the fixed support (701) and the latch (703) and applies an elastic force to drive the latch (703) to rotate until the top-holding portion is located at the position of the locking inclined surface (501a) of the driving block (501) when it is in the upper limit position. The latch block (705) is mounted on the fixed support (701) and can move linearly up and down. The lever (706) is fixed to the latch block (705). The sixth return spring (707) is arranged on the fixed support (701) and applies an elastic force to the latch block (705) to drive it to move leftward until it abuts against the rotation-blocking portion of the latch (703) and blocks the rotation of the latch (703). The middle of the push arm (708) is hinged to the fixed support (701), its first end is located below the lever (706), and its second end is used to contact the wedge block (709). The wedge block assembly is mounted on the passive slider (4) and includes a wedge block (709) and a telescopic driving portion for driving the wedge block (709) to be in an extended or retracted state. The holding support plate (722) is connected to the driving block (501) and is located above the transition surface (501c). When the linear slider (3) is in its upper limit position, the top-holding portion of the latch (703) presses on the locking inclined surface (501a), and when the passive slider (4) is also in its upper limit position, the wedge block (709) is located above the second end of the push arm (708). When the passive slider (4) moves downward from the upper limit position, the wedge block (709) in the extended state will push the second end of the push arm (708) to rotate, and when the push arm (708) rotates, the first end will push the lever (706) to move the latch block (705) to move away from the rotation limit of the latch (703). When the holding support plate (722) moves downward with the passive slider (4), it can abut against both the top-holding portion and the second end of the push arm (708) to prevent the latch (703) from resetting and rotating and the latch block (705) from resetting and moving downward. When the linear slider (3) is in its upper limit position and the passive slider (4) moves upward to its upper limit position, the extending trigger structure triggers the telescopic driving portion to move downward relative to the passive slider (4) to the in-place position so that the wedge block (709) is in the extended state.

6. The crank connecting rod motion device according to claim 5, characterized in that: The position holding mechanism (7) further includes a retraction trigger structure. When the wedge block (709) moves downward with the passive slider (4) and is located below the pushing arm (708), and when the passive slider (4) reaches its lower limit position, the retraction trigger structure triggers the telescopic drive part to move upward relative to the passive slider (4) to a position where the wedge block (709) is in a retracted state.

7. The crank connecting rod motion device according to claim 6, characterized in that: The telescopic drive part of the wedge block assembly includes a bracket (711), a guide frame (710), an action slider (712), a passive action part, and a switching transmission structure. The bracket (711) is fixed on the passive slider (4), the guide frame (710) is fixed to the bracket (711), the wedge block (709) is installed in the guide frame (710) and can move linearly to extend or retract. The action slider (712) is installed on the bracket (711) and can move linearly up and down in the bracket (711). An extension connection structure and a contraction connection structure located below the extension connection structure are provided on the action slider (712). The passive action part is installed on the bracket (711) and is used to be movably connected to the extension connection structure or the contraction connection structure. The switching transmission structure connects the passive action part and the wedge block (709). When the action slider (712) moves downward relative to the bracket (711), the passive action part moves to the position of the extension connection structure, and the switching transmission structure drives the wedge block (709) to change to an extended state. When the action slider (712) moves upward relative to the bracket (711), the passive action part moves to the position of the contraction connection structure, and the wedge block (709) changes to a retracted state. The extension trigger structure and the retraction trigger structure respectively include an extension upper convex platform and a retraction lower convex platform. When the linear sliding part (3) is at the upper limit position, the upper end of the action slider (712) abuts against the extension upper convex platform. When the wedge block assembly moves downward with the passive slider (4), the lower end of the action slider (712) will abut against the retraction lower convex platform.

8. The crank connecting rod motion device according to claim 7, characterized in that: The extending connection structure and the retracting connection structure on the moving slider (712) respectively include a first cylindrical concave surface (712b) and a second cylindrical concave surface (712a), and the first cylindrical concave surface (712b) and the second cylindrical concave surface (712a) are connected by an inclined surface. The passive moving part is a moving wheel (713). The moving wheel (713) can be placed in the first cylindrical concave surface (712b) and the second cylindrical concave surface (712a) and can move between the two. The switching transmission structure includes a first switching swing arm (714), a second switching swing arm (716), a switching connecting rod (715) and a lifting wheel (717). The middle parts of the first switching swing arm (714) and the second switching swing arm (716) are rotatably installed on the bracket (711). One end of the first switching swing arm (714) is connected to the moving wheel (713), and the other end is hinged to one end of the switching connecting rod (715). The other end of the switching connecting rod (715) is hinged to one end of the second switching swing arm (716). The other end of the second switching swing arm (716) is connected to the lifting wheel (717). The lifting wheel (717) abuts against one end of the wedge block (709). When the moving wheel (713) moves from the second cylindrical concave surface (712a) to the first cylindrical concave surface (712b), the lifting wheel (717) jacks up the wedge block (709) to the extended state. The wedge block assembly further includes a seventh return spring (718) installed on the bracket (711). The seventh return spring (718) acts on the wedge block (709) to provide an elastic force to drive the wedge block (709) to reset to the retracted state.

9. The crank connecting rod motion device according to claim 2, characterized in that: The position holding mechanism (7) includes a guide wheel set (702). The guide wheel set (702) includes a plurality of guide wheels arranged linearly in the up and down directions. The inner side of the driving block (501) abuts against the passive slider (4), and the outer side of the driving block (501) can abut against the guide wheel set (702) when the driving block (501) moves downward.

10. The crank connecting rod motion device according to claim 2, characterized in that: The driving block (501) is connected to the linear sliding member (3) through a flexible connection assembly (8). The flexible connection assembly (8) includes a connection block (802) and a transfer block (801). The connection block (802) is rotatably connected to the linear sliding member (3), and the rotation axis is perpendicular to the rotation plane of the crank (1). The upper end of the transfer block (801) is pivotally connected to the connection block (802), and the lower end is pivotally connected to the driving block (501). The rotation axis between the transfer block (801) and the connection block (802) is perpendicular to the moving direction of the linear sliding member (3) and perpendicular to the rotation axis between the connection block (802) and the linear sliding member (3). The rotation axis between the transfer block (801) and the driving block (501) is parallel to the rotation axis between the connection block (802) and the linear sliding member (3).

11. A power device includes a cylinder piston device. The cylinder piston device includes a cylinder (11), a piston (9) located in the cylinder (11), and a piston rod (10) connected to the piston (9). It is characterized in that: It further includes a crank and connecting rod motion device as described in any one of claims 1 to 10, and the linear sliding member (3) of the crank and connecting rod motion device is fixedly connected to or integral with the piston rod (10).

12. The power device according to claim 11, characterized in that: The cylinder (11) is provided with a core inner hole (11i) and an N-stage sleeve inner hole (11j) in sequence from top to bottom, where N≥1, and the cross-section increases in sequence from the core inner hole (11i) to the N-stage sleeve inner hole (11j). There are inter-stage stepped surfaces (11e) between the core inner hole (11i) and the uppermost first-stage sleeve inner hole (11j), and between adjacent two-stage sleeve inner holes (11j); the piston (9) includes a piston core (92) and an N-stage piston sleeve (91) from inside to outside in sequence. The innermost first-stage piston sleeve (91) is sleeved on the piston core (92) and can move relatively up and down. When N≥2, the outer-stage piston sleeve (91) is sleeved on the inner-stage piston sleeve (91) and can move relatively up and down. Inner piston rings are provided between the piston core (92) and the first-stage piston sleeve (91), and between adjacent two-stage piston sleeves (91). The lower end of the piston core (92) is connected to the piston rod (10). The piston core (92) and the first-stage piston sleeve (91) are respectively provided with a first limit stop surface (92a) and a second limit stop surface (91a), and the piston core (92) can move upward relative to the first-stage piston sleeve (91) until the first limit stop surface (92a) abuts against the second limit stop surface (91a). The adjacent two-stage piston sleeves (91) are respectively provided with a third limit stop surface and a fourth limit stop surface, and the inner-stage piston sleeve (91) can move upward relative to the outer-stage piston sleeve (91) until the third limit stop surface and the fourth limit stop surface abut against each other; the N-stage piston sleeve (91) is located in the N-stage sleeve inner hole (11j). When the piston core (92) is at its top dead center, the upper end of the piston core (92) is located in the core inner hole (11i), and the upper ends of the i-stage piston sleeves (91) are respectively located in the i-stage sleeve inner holes (11j), where N≥i≥1, and the first limit stop surface (92a) of the piston core (92) and the second limit stop surface (91a) of the first-stage piston sleeve (91) abut against each other, and the third limit stop surface and the fourth limit stop surface of the adjacent two-stage piston sleeves (91) abut against each other;The cylinder piston device further includes a sleeve locking mechanism (13), a force transmission mechanism, and a force transmission release mechanism. The force transmission mechanism is respectively provided on the piston core (92) and the piston sleeves (91) within the Nth stage. The force transmission mechanism includes a force transmission pin (14) disposed in a force transmission pin hole (92b) on the outer side surface of the piston core (92) or the piston sleeve (91), and a force transmission elastic structure acting on the force transmission pin (14). The force transmission pin (14) can move in the force transmission pin hole (92b) to extend or retract into the force transmission pin hole (92b). The force transmission elastic structure applies an elastic force to the force transmission pin (14) to drive the force transmission pin (14) to move outward. When the first limit stop surface (92a) of the piston core (92) abuts against the second limit stop surface (91a) on the first-stage piston sleeve (91), the force transmission pin (14) on the piston core (92) is located above the lower end surface of the piston sleeve (91). When the third limit stop surface and the fourth limit stop surface of two adjacent piston sleeves (91) abut against each other, the force transmission pin (14) on the inner piston sleeve (91) is located above the lower end surface of the outer piston sleeve (91); when the piston core (92) reaches the top dead center, the positions of all the piston sleeves (91) can be locked by the sleeve locking mechanism (13). When the piston core (92) descends from its top dead center to a position where the upper end of the force transmission pin (14) on it reaches the lower end surface of the first-stage piston sleeve (91), the force transmission pin (7) extends out of the force transmission pin hole (12b) and the sleeve locking mechanism (13) releases the locking of this piston sleeve (91). When the inner piston sleeve (91) of two adjacent piston sleeves (91) descends from its top dead center to a position where the upper end of the force transmission pin (14) on it reaches the lower end surface of the outer piston sleeve (91), the force transmission pin (7) extends out of the force transmission pin hole (12b) and the sleeve locking mechanism (13) releases the locking of the outer piston sleeve (91); when the piston core (92) descends to its bottom dead center, the force transmission release mechanism contacts the force transmission pin (14) in the extended state and compresses the force transmission pin (14) into the force transmission pin hole (92b).; 13. The power device according to claim 12, wherein: The cylinder (11) is provided with an unlocking pin through hole (11f), a retaining pin through hole (11h) and a locking pin through hole (11g), and the retaining pin through hole (11h) is located below the locking pin through hole. The sleeve locking mechanism (13) includes a force transmission plate (13a), a locking elastic structure, an unlocking pin (13b), a retaining pin (13d) and a locking pin (13c). The unlocking pin (13b), the retaining pin (13d) and the locking pin (13c) are respectively located in the unlocking pin through hole (11f), the retaining pin through hole (11h) and the locking pin through hole (11g). The outer ends of the unlocking pin (13b), the retaining pin (13d) and the locking pin (13c) are all connected to the force transmission plate (13a) and move with the force transmission plate (13a). The locking elastic structure applies an elastic force to the force transmission plate (13a) to drive the force transmission plate (13a) to press against the outer wall of the cylinder (11). At this time, the inner ends of the unlocking pin (13b), the retaining pin (13d) and the locking pin (13c) all extend into the cylinder (11). When the force transmission plate (13a) approaches or moves away from the cylinder (11), the unlocking pin (13b), the retaining pin (13d) and the locking pin (13c) can synchronously extend or retract into the inner wall of the cylinder (11). The sleeve locking mechanism (13) is N in number and is used to lock N - stage piston sleeves (91) respectively. When the piston sleeve (91) is at the top dead center, the locking pin (13c) of its corresponding sleeve locking mechanism (13) abuts against the lower end face of the piston sleeve (91). An unlocking block (15) is fixedly arranged on the piston core (92), and when N≥2, an unlocking block (15) is also fixedly arranged on the piston sleeve (91) within the N - th stage. An unlocking inclined surface (15a) is arranged on the lower side of the unlocking block (15). When the piston core (92) moves downward from its top dead center, the unlocking inclined surface (15a) of the unlocking block (15) on it can contact the unlocking pin (13b) of the sleeve locking mechanism (13) for locking the i - th stage piston sleeve (91) and drive the unlocking pin (13b) to move outward until it retracts into the inner wall of the cylinder (11). When N≥2, when the inner piston sleeve (91) of two adjacent - stage piston sleeves (91) moves downward from its top dead center, the unlocking inclined surface (15a) of the unlocking block (15) on it can contact the unlocking pin (13b) of the sleeve locking mechanism (13) for locking the outer piston sleeve (91) and drive the unlocking pin (13b) to move outward until it retracts into the inner wall of the cylinder (11). When the piston sleeve (91) leaves its top dead center, at least one of the unlocking pin (13b), the retaining pin (13d) and the locking pin (13c) of its corresponding sleeve locking mechanism (13) abuts against the outer peripheral surface of the piston sleeve (91).

14. A method for operating a piston engine, characterized in that: The piston engine includes the power device as described in any one of claims 11 to 13, and further includes an intake valve, an exhaust valve and an ignition device. When the passive slider in the power device is at its lower limit position, the angle corresponding to the crank is the bottom dead center angle. The piston engine operation method includes the following processes: A1. Exhaust stroke process: The exhaust valve opens, the crank (1) rotates from the bottom dead center angle towards the transmission disconnection angle, the clutch mechanism (6) remains in the transmission connection state, the piston rod (10) moves upward from its bottom dead center, the piston (9) discharges the exhaust gas in the cylinder (11). When the crank (1) reaches the transmission disconnection angle, the piston rod (10) reaches its top dead center, and the position holding mechanism (7) locks the position of the piston rod (10), and the clutch mechanism (6) switches to the transmission disconnection state; A2. Intake waiting process: The clutch mechanism (6) remains in the transmission disconnection state, the crank (1) rotates from the transmission disconnection angle to the zero phase angle and then to the transmission connection angle, the piston rod (10) remains at its top dead center. When the crank (1) reaches the transmission connection angle, it switches to the transmission connection state, the exhaust valve closes, and the intake valve opens; A3. Intake stroke process: The crank (1) rotates from the transmission connection angle towards the bottom dead center angle, the clutch mechanism (6) remains in the transmission connection state, the piston (9) moves downward. When the crank (1) reaches the bottom dead center angle, the piston rod (10) reaches its bottom dead center, and the intake valve closes; A4. Compression stroke process: The crank (1) rotates from the bottom dead center angle towards the transmission disconnection angle, the clutch mechanism (6) remains in the transmission connection state, the piston rod (10) moves upward, the piston (9) compresses the gas in the cylinder (11). When the crank (1) reaches the transmission disconnection angle, the piston rod (10) reaches its top dead center, and the position holding mechanism (7) locks the position of the piston rod (10), and the clutch mechanism (6) switches to the transmission disconnection state; A5. Waiting for ignition and combustion delay process: The crank (1) rotates from the transmission disconnection angle to the zero phase angle and then to the transmission connection angle, the piston rod (10) remains at its top dead center. Ignition is carried out at any time point during this period. When the crank (1) reaches the transmission connection angle, it switches to the transmission connection state; A6. Power stroke process: The clutch mechanism (6) remains in the transmission connection state, the high-pressure gas in the cylinder (11) drives the piston (9) to move downward, the piston rod (10) drives the crank (1) to rotate from the transmission connection angle to the bottom dead center angle, and the piston rod (10) reaches its bottom dead center.

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