A harmonic inertia tuned piston connecting rod assembly and reciprocating mechanism

Abstract

The application provides a harmonic frequency type inertial tuning piston connecting rod assembly and reciprocating mechanism, and relates to the technical field of reciprocating machinery. The piston and the connecting rod are hinged through a pin shaft, the pin shaft is a hollow structure, a vibrating hammer is arranged in the internal cavity of the pin shaft, and an activity gap is left between the vibrating hammer and the inner wall of the pin shaft. The application is reasonable in design. In the process of equal acceleration and equal deceleration of the crankshaft, the power consumption of reciprocating motion is mainly concentrated in the moment of the upper and lower dead points, at this time, the driving arm of the crankshaft is zero or very small, and the transmission and consumption of the acceleration inertia force reach the peak value. The vibrating hammer with high hardness and low weight is arranged in the internal cavity of the pin shaft, when the piston runs to the upper and lower dead points, the vibrating hammer continues to slide forward and hits the inner side of the pin shaft due to inertia, converts the momentum into reverse impact force and transmits the impact force to the piston, provides starting assistance in the critical moment of the maximum consumption of the crankshaft, and makes the reversing process more light and quick.

Description

Technical Field

[0001] This invention relates to the field of reciprocating motion machinery technology, specifically to a harmonic inertial tuning piston-connecting rod assembly and a reciprocating motion mechanism. Background Technology

[0002] In reciprocating piston engines, compressors, and other power machinery, the connecting rod, as the core transmission component connecting the piston and crankshaft, directly affects the overall efficiency, vibration and noise levels, and service life of the machine. In traditional designs, the small end of the connecting rod (the end connected to the piston) is hinged to the piston head via a piston pin. The pin hole typically only contains a lubrication structure, a snap ring limiting structure, or a simple anti-friction bushing. Its function is mainly focused on ensuring the flexibility and wear resistance of the hinge, and it does not have active energy management or power assistance functions.

[0003] For a long time, a common technical bias has existed in the design of reciprocating mechanisms: the belief that increasing the mass of reciprocating components inevitably leads to increased inertial forces, thereby increasing power consumption and reducing mechanical efficiency. Based on this understanding, existing optimization directions mainly focus on the following aspects: First, replacing traditional steel with lightweight materials (such as aluminum alloys, titanium alloys, and carbon fiber composites) to reduce the weight of connecting rods and pistons; second, reducing reciprocating acceleration and thus inertial forces by optimizing the geometric parameters of crank-connecting rod mechanisms (such as connecting rod ratio and crank radius); and third, using structures such as balance shafts and double counterweights to externally compensate for reciprocating inertial forces. All of these technical solutions follow the basic logic of "weight reduction equals energy saving," and no one has yet proposed a technical approach that utilizes the inertial forces of the reciprocating components themselves to assist in work.

[0004] On the other hand, to improve the vibration characteristics of reciprocating motion components, some existing technologies have incorporated dynamic vibration absorbers inside the piston pin. The core principle of these existing dynamic vibration absorbers is to flexibly connect the mass block to the piston pin using elastic elements (springs, viscoelastic materials, etc.), forming a vibration subsystem with a specific natural frequency. When the system is subjected to external excitation forces, the mass block undergoes forced vibration, and the vibration energy is converted into heat energy and dissipated through elastic damping elements, thereby achieving vibration reduction and noise reduction. In these solutions, the movement of the mass block is passive, continuous, and energy-consuming; its functional positioning remains limited to "eliminating" or "suppressing" harmful vibrations, failing to break free from the traditional cognitive framework of "increased mass leading to energy consumption."

[0005] Furthermore, in traditional reciprocating piston mechanisms, when the piston reaches top dead center or bottom dead center, its instantaneous velocity is zero. At this point, the crankshaft and connecting rod are collinear, and the driving force arm applied by the crankshaft is zero or minimal. To overcome the inertia of the reciprocating mass of the piston itself and the small end of the connecting rod, the crankshaft must output a very large torque at the moment of reversal to complete the starting steering. This process leads to a significant reduction in mechanical efficiency during the reversal phase and serious energy waste. Summary of the Invention

[0006] 1. The technical problem that the invention aims to solve: This invention provides a harmonic inertial tuning piston rod assembly and a reciprocating motion mechanism to solve the technical problems existing in the background art.

[0007] 2. Technical Solution: To achieve the above objectives, the present invention provides the following technical solution: a harmonic inertial tuning piston-connecting rod assembly, comprising a piston, a connecting rod, and a pin, wherein the piston and the connecting rod are hinged together by the pin, and the pin is a hollow structure. The pin is characterized in that: a vibrating hammer is disposed within the internal cavity of the pin, a clearance is provided between the vibrating hammer and the inner wall of the pin, and limit structures are respectively provided at both ends of the pin to restrict the vibrating hammer from sliding freely in the radial direction, preventing it from moving axially.

[0008] Furthermore, the limiting structure is a retaining ring disposed at both ends of the pin.

[0009] Furthermore, the limiting structure consists of a limiting step disposed at one end of the pin and a retaining ring disposed at the other end of the pin.

[0010] Furthermore, the vibrating hammer has a cylindrical structure or a hollow annular structure.

[0011] Furthermore, the piston has symmetrically provided fixing grooves on its lateral solid portion, and a second limiting ring is provided in the fixing groove, and a vibrating hammer is installed in the second limiting ring.

[0012] Furthermore, at least one limiting hole is provided on the body of the connecting rod, and the opening direction of the limiting hole is located on the perpendicular line between the connecting rod body and the pin shaft. A vibrating hammer is installed in the limiting hole.

[0013] Furthermore, the vibratory hammer is made of a high-hardness, low-weight material, which is any one of mold steel, titanium alloy, or aluminum alloy.

[0014] Furthermore, the vibratory hammer has an oil passage hole, which is arranged radially through the vibratory hammer.

[0015] This application also protects a reciprocating motion mechanism whose structure includes the piston-connecting rod assembly described above.

[0016] 3. Beneficial effects: Compared with the prior art, the technical solution provided by this invention has the following advantages: This invention is rationally designed. By placing a freely sliding vibrating hammer inside the cavity of the crankshaft, the inertial impact of the hammer near the piston's top and bottom dead centers generates a reverse assist, making piston reversal and starting smoother and effectively reducing the driving torque requirement of the crankshaft at dead center positions. During the intermediate stroke, the direction of acceleration continuously changes with the crankshaft's rotation; during the acceleration phase, the vibrating hammer, due to inertial lag, feeds back its stored kinetic energy to the crankshaft, achieving energy recycling.

[0017] This invention overcomes the technical bias in traditional reciprocating motion mechanism design that "increasing the reciprocating mass inevitably increases power consumption." During the constant acceleration and deceleration of the crankshaft, the power consumption of the reciprocating motion is mainly concentrated at the moments of top and bottom dead centers—similar to the principle that a car struggles the most when starting but runs smoothly once it reaches its destination. At this point, the crankshaft drive arm is zero or minimal, and the power consumption due to acceleration inertia reaches its peak. This invention incorporates a high-hardness, low-weight vibrating hammer within the internal cavity of the piston pin. When the piston reaches its top or bottom dead center, there is a gap between the vibrating hammer and the piston pin. Due to inertia, the vibrating hammer continues to slide forward and impacts the inner side of the piston pin. After the impact, it moves in the opposite direction and impacts the inner wall of the other side of the piston pin, converting its momentum into a reverse impact force that is transmitted to the piston. This provides starting assistance at the critical moment when crankshaft power consumption is at its highest, making the reversing process smoother.

[0018] Meanwhile, the vibratory hammer floats freely during the mid-stroke phase, consuming only a minimal amount of acceleration energy. During the deceleration phase after passing dead center (90 degrees), this stored kinetic energy is fed back to the crankshaft through a limiting structure, achieving energy recycling. The low-mass, high-rigidity vibratory hammer can still generate significant impact force after withstanding frequent impacts, effectively offsetting the power consumption of reciprocating motion. Its low-mass characteristics ensure that the overall increase in power consumption is extremely limited. In summary, the assist provided by the vibratory hammer at critical commutation moments far outweighs the small amount of energy consumed during the mid-stroke phase, achieving overall energy saving, efficiency improvement, and reduced crankshaft drive torque requirements.

[0019] The combination of annular elastic layer and hard excitation ring provides a larger effective movement space for the vibratory hammer without increasing the fitting clearance. At the same time, the buffering effect of the elastic layer effectively absorbs the high-frequency components in the impact energy, avoiding impact noise caused by excessive clearance.

[0020] This invention allows the lubricating medium to flow freely within the internal cavity of the pin by creating a radially penetrating oil passage on the vibratory hammer. This ensures that the contact surface between the vibratory hammer and the inner wall of the pin is adequately lubricated, effectively preventing wear and aging caused by insufficient oil and extending the service life.

[0021] It should be noted that the structures not described in this invention are not related to the design points and improvement directions of this invention, and are the same as or can be implemented using existing technologies, so they will not be elaborated here. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention; Figure 2 This is a schematic diagram of the structure of Embodiment 2 of the present invention; Figure 3 This is a schematic diagram of the structure of Embodiment 3 of the present invention; Figure 4 This is a schematic diagram of the structure of Embodiment 4 of the present invention; Figure 5 This is a schematic diagram of the structure of Embodiment 5 of the present invention; Figure 6 This is a schematic diagram of the structure of Embodiment Six of the present invention; Figure 7 This is a schematic diagram of the exploded structure of Embodiment 3 of the present invention.

[0023] Figure label: 1. Piston; 2. Connecting rod; 3. Pin; 31. Annular elastic layer; 32. Hard excitation ring; 4. Vibration hammer; 5. Limiting structure; 6. Fixing groove; 7. Limiting hole; 8. Oil passage hole. Detailed Implementation

[0024] To facilitate understanding of the present invention, a more complete description of the invention will be given below with reference to the accompanying drawings, which illustrate several embodiments of the invention. However, the invention can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided so that the disclosure of the invention will be more thorough and complete.

[0025] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0026] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0027] In this invention, unless otherwise explicitly specified and limited, the terms "installed," "connected," "linked," "fixed," "provided with," and "located in" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0028] It should be noted that structures not described in this invention do not involve the design points and improvement directions of this invention, and can all be achieved using existing technologies known to those skilled in the art.

[0029] The specific implementation of the present invention will be described in detail below with reference to specific embodiments.

[0030] See attached document Figure 1-7 This invention provides a harmonic-frequency inertial tuning piston-connecting rod assembly, which includes a piston 1, a connecting rod 2, and a pin 3. The piston 1 and connecting rod 2 are hinged together by the pin 3, which is a hollow structure with a vibrating hammer disposed within its internal cavity. The core design concept of this application is to utilize the inertial motion of the vibrating hammer sliding freely within the pin 3 to generate a reverse impact force when the piston 1 moves near its top and bottom dead centers, providing starting assistance for the piston 1 during reversal and feeding kinetic energy back to the crankshaft during acceleration, thereby achieving energy saving and efficiency improvement. Several embodiments are described in detail below with reference to the accompanying drawings. Example 1

[0031] Reference Figure 1 This application provides a harmonic-frequency inertial tuning piston-connecting rod assembly, including a piston 1, a connecting rod 2, and a pin 3. The connecting rod 2 has a small end and a large end, with a pin hole at the small end for connection to the piston 1. The piston 1 also has a pin hole extending axially along the crankshaft. The pin 3 passes through the pin hole at the small end of the connecting rod 2 and the pin hole in the piston 1, hinged to the piston 1 as a single unit.

[0032] The pin 3 is a hollow tubular structure with an axially extending internal cavity. A vibrating hammer 4 is housed within this cavity. The vibrating hammer 4 is an independent component, its shape adapted to the internal cavity of the pin 3. The vibrating hammer 4 can be a solid cylindrical structure or a hollow annular structure. When a hollow annular structure is used, the vibrating hammer 4 has a through hole at its center, but this through hole is only for weight reduction or inertia adjustment and is not used to pass through other components. The outer diameter of the vibrating hammer 4 is smaller than the inner diameter of the pin 3, thus forming a certain annular clearance between the outer circumference of the vibrating hammer 4 and the inner wall of the pin 3. This clearance allows the vibrating hammer 4 to slide freely radially within the pin 3, while allowing it to remain in a non-contact state or only have very slight contact with the inner wall of the pin 3.

[0033] The clearance between the vibratory hammer 4 and the inner wall of the pin 3 is preferably 0.05 to 0.2 mm. This ensures that the vibratory hammer 4 can slide freely inside the pin 3 without making continuous rigid contact with the inner wall of the pin 3; at the same time, the clearance cannot be too large, otherwise the movement of the vibratory hammer 4 inside the pin 3 will be too violent, which may generate unacceptable impact noise and affect the stable operation of the system.

[0034] Limiting structures 5 are provided at both ends of the pin 3 to restrict the axial movement of the vibratory hammer 4, so that the vibratory hammer 4 can only slide freely in the radial direction.

[0035] exist Figure 1 In the specific embodiment shown, the limiting structure 5 is a retaining ring disposed at both ends of the pin 3. The retaining ring partially extends into the retaining ring groove at the end of the pin 3, forming an axial block at the port of the pin 3. The retaining ring is a standard part, which is easy to install, inexpensive, and suitable for mass production.

[0036] The vibratory hammer 4 is made of a high-hardness, low-weight material. This high-hardness, low-weight material can be any one of mold steel, titanium alloy, or aluminum alloy. The high hardness of the material prevents wear and deformation of the hammer's end face during frequent impacts with the limiting structure, ensuring the stability of the assist effect during long-term operation and reducing maintenance and replacement frequency. The low weight characteristic allows the hammer to float more flexibly within the pin shaft, with low starting inertia and faster response, enabling it to quickly generate impact assistance at the optimal time at the upper and lower dead centers. Simultaneously, it reduces contact pressure and friction loss on the inner wall of the pin shaft, further reducing power consumption during the intermediate stroke. Example 2

[0037] Figure 2 The diagram shown is a structural schematic of another embodiment of this application, which is in Figure 1 Based on the basic structure shown, a tremor hammer is added to the connecting rod 2.

[0038] Reference Figure 2In this embodiment, a vibrating hammer 4 is disposed in the internal cavity of the pin 3, and the two ends of the pin 3 are axially positioned by snap rings for the vibrating hammer 4. Its structure is similar to... Figure 1 The same as the first embodiment shown.

[0039] Based on this, a limiting hole 7 is formed on the body of connecting rod 2. The body of connecting rod 2 refers to the long shank portion connecting the small end and the large end of connecting rod 2. The limiting hole 7 is formed inside the solid material of the body of connecting rod 2. The limiting hole 7 is formed in the direction of the perpendicular line between the body of connecting rod 2 and the pin 3, that is, the limiting hole 7 extends in the transverse direction of the body of connecting rod 2, and its length direction is perpendicular to the axis of pin 3 and also perpendicular to the length direction of the body of connecting rod 2.

[0040] A vibrating hammer 4 is installed inside the limiting hole 7. There is a clearance between the vibrating hammer 4 and the inner wall of the limiting hole 7. Limiting structures 5 are also provided at both ends of the limiting hole 7, so that it can only slide radially. During the swing of the connecting rod 2, the vibrating hammer uses inertial force to generate vibration assistance, which works in conjunction with the vibrating hammer 4 to assist the piston 1 in reversing. Example 3

[0041] Figure 3 The diagram shown is a structural schematic of another embodiment of this application, in which... Figure 1 Based on the basic structure shown, two additional vibrating hammers are installed in the vertical direction of the connecting rod 2.

[0042] Reference Figure 3 and Figure 7 In this embodiment, a vibrating hammer 4 is disposed in the internal cavity of the pin 3, and the two ends of the pin 3 are axially positioned by snap rings for the vibrating hammer 4. Its structure is similar to... Figure 1 The same as the first embodiment shown.

[0043] Based on this, two limiting holes 7 are made at intervals along the vertical direction on the body of connecting rod 2. The two limiting holes 7 are arranged vertically along the length of the connecting rod 2, that is, one limiting hole 7 is close to the small end of connecting rod 2, and the other limiting hole 7 is close to the large end of connecting rod 2. A vibrating hammer 4 is installed in each limiting hole 7.

[0044] The two limiting holes 7 are both located in the direction of the perpendicular line between the connecting rod 2 and the pin 3, that is, each limiting hole 7 extends in the transverse direction of the connecting rod 2. The two vibrating hammers 4 slide radially in their respective limiting holes 7, using the inertial force of the connecting rod 2 during the swinging process to generate vibration assistance.

[0045] By setting two vibrating hammers 4 in the vertical direction of the connecting rod 2, an assist effect can be generated at different swing phases of the connecting rod 2, making the assist effect more uniform and continuous throughout the entire stroke range, and further enhancing the energy-saving and efficiency-enhancing technical effect.

[0046] The two vibrating hammers 4 can be made of the same material and size, or they can be a combination of different materials and sizes. For example, the vibrating hammer 4 closer to the smaller end of the connecting rod 2 can have a smaller mass to respond to the high-frequency oscillation component; the vibrating hammer 4 closer to the larger end of the connecting rod 2 can have a larger mass to respond to the low-frequency, large-amplitude oscillation component. This differentiated design can optimize the assist effect across the entire frequency range. Example 4

[0047] Figure 4 The diagram shown is a structural schematic of another embodiment of this application, in which... Figure 1 Based on the basic structure shown, two additional vibrating hammers are symmetrically installed on both sides of the piston head 1.

[0048] Reference Figure 4 In this embodiment, a vibrating hammer 4 is disposed in the internal cavity of the pin 3, and the two ends of the pin 3 are axially positioned by snap rings for the vibrating hammer 4. Its structure is similar to... Figure 1 The same as the first embodiment shown.

[0049] Based on this, two fixing grooves 6 are symmetrically formed on the lateral solid portion of the piston 1. The lateral solid portion of the piston 1 refers to the solid material area on the piston 1 body located around the pin hole, which has sufficient structural strength to accommodate the additional vibrating hammer structure. The two fixing grooves 6 are located on both sides of the pin 3, that is, one fixing groove 6 is formed on the left and one on the right side of the piston 1, and the two fixing grooves 6 are symmetrically arranged with respect to the axis of the pin 3.

[0050] Each fixing groove 6 is symmetrically equipped with a second limiting ring, which is fixedly installed inside the fixing groove 6. The second limiting ring is a ring-shaped component and can be fixed in the fixing groove 6 by interference fit, threaded connection, or snap-fit. A vibrating hammer is installed on the inner side of each second limiting ring. The vibrating hammer is restricted to radial sliding between the inner walls of the second limiting ring and cannot slide axially.

[0051] The advantage of symmetrically arranging two vibrating hammers on the left and right sides of piston 1 is that the movements of the two hammers are independent of each other. When piston 1 reverses direction, a boosting impulse can be generated from both sides simultaneously, so that the boosting force acts more evenly on the piston body and avoids generating additional lateral overturning torque. At the same time, the symmetrical arrangement is conducive to the dynamic balance of piston 1 and reduces the additional vibration caused by the movement of the hammers.

[0052] The direction in which the fixing groove 6 is opened can be parallel to the axial direction of the pin 3, or other directions can be selected according to actual needs. In addition to being arranged symmetrically, multiple fixing grooves 6 can also be evenly distributed along the circumference of the piston 1 or spaced apart along the axial direction of the pin 3. Example 5

[0053] Figure 5The diagram shown is a structural schematic of another embodiment of this application, which illustrates the combined structure of the pin 3 with an annular elastic layer 31, a hard excitation ring 32 and a vibrating hammer 4.

[0054] Reference Figure 5 In this embodiment, the pin 3 is a hollow tubular structure. An annular elastic layer 31, a rigid excitation ring 32, and a vibrating hammer 4 are disposed in the internal cavity of the pin 3.

[0055] Specifically, an annular elastic layer 31 is disposed between the inner wall of the pin 3 and the rigid excitation ring 32. The annular elastic layer 31 is a ring-shaped elastomer; its outer wall is fitted to the inner wall of the pin 3, and its inner wall is fitted to the outer wall of the rigid excitation ring 32. The rigid excitation ring 32 is a rigid annular component, elastically connected to the pin 3 through the annular elastic layer 31. The annular elastic layer 31 can be made of elastic materials such as rubber, polyurethane, or silicone, and its thickness can be selected according to actual needs, typically ranging from one to eight millimeters. If the thickness of the annular elastic layer 31 is too small, the buffering effect will be insufficient; if the thickness is too large, it may affect the installation space and movement stroke of the rigid excitation ring 32 and the vibrating hammer 4.

[0056] The rigid excitation ring 32 has a hollow cavity inside, and the vibrating hammer 4 is installed inside the rigid excitation ring 32. The limiting structures 5 are provided at both ends of the rigid excitation ring 32. A movable gap is left between the vibrating hammer 4 and the inner wall of the rigid excitation ring 32, allowing the vibrating hammer 4 to move radially along the pin 3 within the space defined by the rigid excitation ring 32. The material, shape, gap, and stroke parameters of the vibrating hammer 4 can be the same as those of the vibrating hammers in the aforementioned embodiments.

[0057] The working principle of this implementation is as follows: When the piston 1 reverses direction, the vibrating hammer 4 strikes the hard excitation ring 32. The impact force is first borne by the hard excitation ring 32, and then transmitted to the pin 3 and piston 1 after being buffered and filtered by the annular elastic layer 31. The annular elastic layer 31 can effectively absorb the high-frequency components in the impact energy, reduce the noise peak, and at the same time store some energy through elastic deformation and release it later, making the assist process smoother and gentler.

[0058] This solution offers an alternative structure to the purely free-sliding vibratory hammer, making it suitable for applications with higher requirements for noise and vibration control. Example 6

[0059] Figure 6 The diagram shown is a structural schematic of another embodiment of this application, which mainly illustrates the specific structure of axial positioning of the vibratory hammer with retaining springs at both ends.

[0060] Reference Figure 6In this embodiment, the vibration hammer 4 inside the pin 3 is used as an example for explanation, but the limiting structure 5 is also applicable to the vibration hammer set in the piston 1 fixing groove 6, the vibration hammer set in the connecting rod 2 limiting hole 7, and the vibration hammer 4 set in the hard excitation ring 32.

[0061] The pin 3 is a hollow tubular structure, and a vibrating hammer 4 is installed in its internal cavity. The outer diameter of the vibrating hammer 4 is smaller than the inner diameter of the pin 3, and there is a clearance between them.

[0062] Each end of the pin 3 is provided with a retaining circlip. The retaining circlip is an elastic annular member with an opening, which is installed in the retaining circlip groove on the inner wall of both ends of the pin 3. The retaining circlip extends partially into the internal cavity of the pin 3, forming an annular axial blocking surface at the port of the pin 3.

[0063] The vibratory hammer 4 is located between two retaining rings, and its radial movement is restricted to the space between the two retaining rings. The retaining rings are easy to install and remove, facilitating the assembly and maintenance of the vibratory hammer. The vibratory hammer 4 can only slide radially within the space formed by the retaining rings.

[0064] In another embodiment, the vibratory hammer 4 has an oil passage hole 8, which extends radially through the vibratory hammer 4 to allow lubricating medium to enter the internal cavity of the pin 3. When there is lubricating medium inside the pin 3, the lubricating medium can flow through the oil passage hole 8, ensuring that the contact surface between the vibratory hammer 4 and the inner wall of the pin 3 is adequately lubricated, effectively preventing wear and aging caused by insufficient oil, and extending the service life of the vibratory hammer 4. At the same time, the presence of the oil passage hole 8 allows the oil to form an appropriate oil film in the internal cavity of the pin 3, playing a role in auxiliary lubrication and noise reduction. It should be noted that the amount of lubricating medium in the internal cavity of the pin 3 should be controlled within an appropriate range to avoid excessive oil forming an excessively thick oil layer, which would produce a damping effect and affect the free sliding and impact response sensitivity of the vibratory hammer 4.

[0065] Description of combinations of various implementation methods above Figures 1 to 6 The various embodiments shown are not mutually exclusive. Where there is no conflict, the technical features of each embodiment can be combined to form more embodiments. For example: The limiting structures 5 at both ends of the vibrating hammer 4 can be adopted Figure 6 The snap ring structure shown can also be a combination structure of limiting step and snap ring.

[0066] Figure 2 The scheme of installing a vibratory hammer on the connecting rod 2 shown can be combined with... Figure 3 The scheme of setting two vibrating hammers 4 on the connecting rod 2 shown can be combined to set three or more vibrating hammers on the connecting rod 2 at the same time.

[0067] Figure 4 The scheme shown, where symmetrically arranged vibrating hammers are mounted on both sides of piston head 1, can be combined with... Figure 2 or Figure 3 The scheme of setting up a vibrating hammer on the connecting rod 2 shown is combined to form an all-round assist scheme in which multiple sets of vibrating hammers are set at both the piston 1 end and the connecting rod 2 end.

[0068] Figure 5 The scheme shown, consisting of an annular elastic layer 31 and a rigid excitation ring 32, can be combined with... Figure 6 The retaining ring limiting structure 5 shown is combined to limit the movement of the vibrating hammer 4 within the rigid excitation ring 32. All variations employing the core inventive concept of this application fall within the protection scope of this application.

[0069] This application also provides a reciprocating motion mechanism, which includes any of the above-mentioned harmonic inertial tuning piston-connecting rod assemblies. This reciprocating motion mechanism can be any type of reciprocating piston engine, such as a four-stroke internal combustion engine or a two-stroke internal combustion engine, or it can be a reciprocating piston compressor, hydraulic pump, or pneumatic motor, etc. Any mechanism that includes a piston, connecting rod, pin, and reciprocating motion system can be improved using the technical solution of this application.

[0070] The working principle of this application will be further explained below with reference to practical applications: During engine or compressor operation, the pin 3 reciprocates linearly along with the piston 1 and connecting rod 2. The vibrating hammer 4, as an independent mass, is enclosed in the internal cavity of the pin 3 and can only slide freely between the limiting structures 5 at both ends, without any elastic element connecting it to the inner wall of the pin 3.

[0071] When piston 1 moves close to top dead center or bottom dead center, the speed of piston 1 and pin 3 decreases to near zero, indicating that they are about to reverse direction. At this time, due to its own inertia, hammer 4 continues to maintain its original direction of motion, sliding at high speed towards the inner wall of pin 3. When hammer 4 strikes the inner wall of pin 3, its momentum is instantly transferred to connecting rod 2 and piston 1 through pin 3, generating a reverse impact force consistent with the new direction of piston 1's movement at the most difficult moment of piston 1's reversal, making piston 1 start more quickly.

[0072] During the intermediate stroke, the piston 1 has a high speed and the speed changes gradually. The vibrating hammer 4 is in a free-floating state inside the pin 3, with only minimal contact friction or fluid resistance between it and the inner wall of the pin 3, consuming almost no main motion power. During the acceleration phase, the vibrating hammer 4 lags behind the movement of the pin 3 due to its mass inertia. Through its interaction with the limiting structure 5, it feeds back the previously stored kinetic energy to the piston 1 and crankshaft, achieving energy recycling.

[0073] The working principle of the vibrating hammer set in the fixed groove 6 of piston 1, the vibrating hammer set in the limiting hole 7 of connecting rod 2, and the vibrating hammer 4 set in the hard excitation ring 32 is the same as that of the vibrating hammer 4—all of them use their own inertia to slide in their respective activity space, hit the limiting structure 5 to generate assistance when changing direction, maintain low loss floating in the middle stroke, and feed back kinetic energy in the acceleration phase.

[0074] The essence of this application lies in breaking through the traditional technical prejudice that "increasing reciprocating mass inevitably increases power consumption," transforming the reciprocating inertial force, originally considered harmful, into an assistive force that helps system operation, thus achieving a functional leap from "passive energy consumption" to "active assistance." The added mass of the vibratory hammer is transformed into assist output at the reversal point, into low-loss floating in the intermediate stroke, and into kinetic energy feedback during the acceleration phase, without increasing overall net power consumption, and can even achieve energy-saving and efficiency-enhancing effects.

[0075] The above-described embodiments are merely illustrative of certain implementations of the present invention, and are described in a relatively specific and detailed manner. However, they should not be construed as limiting the scope of the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements are all within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A harmonic-frequency inertial tuning piston-connecting rod assembly, comprising a piston (1), a connecting rod (2), and a pin (3), wherein the piston (1) and the connecting rod (2) are hinged together by the pin (3), and the pin (3) is a hollow structure, characterized in that: A vibrating hammer (4) is provided in the internal cavity of the pin (3). There is a movable gap between the vibrating hammer (4) and the inner wall of the pin (3). Limiting structures (5) are provided at both ends of the pin (3).

2. The harmonic-frequency inertial tuning piston-connecting rod assembly according to claim 1, characterized in that: The limiting structure (5) is a retaining ring disposed at both ends of the pin (3).

3. The harmonic-frequency inertial tuning piston rod assembly according to claim 1, characterized in that: The limiting structure (5) consists of a limiting step at one end of the pin (3) and a retaining ring at the other end of the pin (3).

4. The harmonic-frequency inertial tuning piston connecting rod assembly according to claim 1, characterized in that: The vibrating hammer (4) has a cylindrical structure or a hollow ring structure.

5. A harmonic-frequency inertial tuning piston-connecting rod assembly according to claim 1, characterized in that: The piston (1) has a symmetrically provided fixing groove (6) on its lateral solid part. A second limiting ring is provided in the fixing groove (6), and the vibrating hammer is installed in the second limiting ring.

6. A harmonic-frequency inertial tuning piston-connecting rod assembly according to claim 1, characterized in that: At least one limiting hole (7) is provided on the rod body of the connecting rod (2). The opening direction of the limiting hole (7) is located on the perpendicular line between the rod body of the connecting rod (2) and the pin (3). The vibrating hammer is installed in the limiting hole (7).

7. A harmonic-frequency inertial tuning piston connecting rod assembly according to claim 1, characterized in that: The pin (3) is also provided with an annular elastic layer (31) and a hard excitation ring (32). The annular elastic layer (31) is disposed between the inner wall of the pin (3) and the hard excitation ring (32). A vibrating hammer (4) is installed inside the hard excitation ring (32). The limiting structure (5) is installed at both ends of the hard excitation ring (32).

8. A harmonic-frequency inertial tuning piston connecting rod assembly according to claim 1, characterized in that: The vibratory hammer (4) is made of a high-hardness, low-weight material, which is any one of mold steel, titanium alloy or aluminum alloy.

9. A harmonic-frequency inertial tuning piston-connecting rod assembly according to claim 1, characterized in that: An oil passage hole (8) is provided on the vibrating hammer (4), and the oil passage hole (8) is arranged to penetrate the vibrating hammer (4) radially.

10. A reciprocating motion mechanism, characterized in that: Includes the harmonic inertial tuning piston rod assembly as described in any one of claims 1 to 9.

Images