CN110307293B - Hydraulic dual-mass flywheel - Google Patents
Hydraulic dual-mass flywheel Download PDFInfo
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- CN110307293B CN110307293B CN201910569215.8A CN201910569215A CN110307293B CN 110307293 B CN110307293 B CN 110307293B CN 201910569215 A CN201910569215 A CN 201910569215A CN 110307293 B CN110307293 B CN 110307293B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
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Abstract
The invention provides a hydraulic dual-mass flywheel, and belongs to the technical field of automobiles. The technical problem that the smoothness of power transmission of an existing dual-mass flywheel structure is poor is solved. The hydraulic dual-mass flywheel comprises a main flywheel and an auxiliary flywheel which are coaxially arranged and can rotate relatively, wherein an oil injection channel with an inlet capable of being communicated with an oil pump is arranged in the main flywheel, an outlet of the oil injection channel faces the auxiliary flywheel, a partition plate extending along the radial direction is arranged on the auxiliary flywheel, and when the main flywheel rotates relative to the auxiliary flywheel, the oil gushed from the outlet of the oil injection channel can be injected on the side face of the partition plate and can push the auxiliary flywheel to rotate. The hydraulic dual-mass flywheel can realize real flexible connection and improve the transmission smoothness.
Description
Technical Field
The invention belongs to the technical field of automobiles, and relates to a hydraulic dual-mass flywheel.
Background
The dual-mass flywheel divides an original flywheel into two parts, one part of the dual-mass flywheel is reserved on the position of one side of an original engine and plays the role of the original flywheel and is used for starting and transmitting the rotating torque of the engine, the other part of the dual-mass flywheel is placed on one side of a transmission system and is used for improving the rotating inertia of the transmission, the other part of the dual-mass flywheel is called a second mass (a secondary mass), and the first mass and the second mass are connected through a spring, so that the torsional vibration and the rolling vibration of a crankshaft of the engine and an input shaft of a transmission box are isolated.
An intelligent magnetorheological fluid dual-mass flywheel with application publication number CN103758923A comprises an outer rotor component, magnetorheological fluid, an inner rotor, an excitation device and a dual-mass flywheel component. The outer rotor assembly is installed on the left side of the dual-mass flywheel assembly, a sealing cavity rear cover in the outer rotor assembly is fixedly connected with a first flywheel bolt in the dual-mass flywheel assembly, the inner rotor is sleeved on a second flywheel stepped shaft of a second flywheel in the dual-mass flywheel assembly and is connected through a spline pair, the inner rotor is installed inside the outer rotor assembly, a working gap formed by the outer circle surface of the inner rotor and the gap between the sealing cavity front cover in the outer rotor assembly and the inner circle surface of the sealing cavity rear cover is a sealing cavity, magnetorheological fluid is filled in the sealing cavity, and the excitation device is fixedly installed around the outer rotor assembly.
The double-mass flywheel structure is characterized in that magnetorheological fluid is arranged in the traditional double-mass flywheel, vibration transmission is reduced to a certain degree, but a reaction force is inevitably generated after the spring is compressed, and under the interaction of the positive and the reaction forces, the double-mass flywheel self inevitably has a resonance frequency which is determined by the design structure of the double-mass flywheel and cannot be eliminated, so that the smooth effect of power transmission is influenced. And those skilled in the art will consider solutions to this problem as follows: the mass proportion of the first mass and the second mass is reasonably distributed to reduce the resonance rotating speed below the idle rotating speed, so that the resonance rotating speed can be crossed only when the engine is just started and stopped, the resonance rotating speed is out of the rotating speed range of the engine, and the smoothness is improved; or improving the mechanical characteristics of the spring to improve the transmission and shock absorption effects; or to improve the output stability of the engine itself.
Disclosure of Invention
The invention provides a hydraulic dual-mass flywheel aiming at the problems in the prior art, and the technical problems to be solved by the invention are as follows: how to improve the power transmission smoothness of the flywheel.
The purpose of the invention can be realized by the following technical scheme:
a hydraulic dual-mass flywheel comprises a main flywheel and an auxiliary flywheel which are coaxially arranged and can rotate relatively, wherein an oil injection channel with an inlet capable of being communicated with an oil pump is arranged in the main flywheel, an outlet of the oil injection channel faces the auxiliary flywheel, a partition plate extending along the radial direction is arranged on the auxiliary flywheel, and when the main flywheel rotates relative to the auxiliary flywheel, the oil gushing out from the outlet of the oil injection channel can be injected to the side face of the partition plate and can push the auxiliary flywheel to rotate.
The main flywheel is used for being connected with the crankshaft and synchronously rotating, stores energy and transmits the rotating torque of the engine when rotating, and the auxiliary flywheel is used for being matched with the clutch and placed on one side of a transmission system so as to improve the rotating inertia of the transmission. By arranging the oil injection channel on the main flywheel, the inlet of the nozzle channel can be communicated with an oil pump of an engine, therefore, when the engine runs, the oil pump can pump high-pressure oil into the oil injection channel, the auxiliary flywheel is provided with the partition plate, the outlet of the oil injection channel faces the auxiliary flywheel, the high-pressure oil gushing from the oil injection channel can be sprayed towards the auxiliary flywheel, the main flywheel rotates at a high speed relative to the auxiliary flywheel, so that the sprayed high-pressure engine oil can continue to move along the tangential direction under the inertia effect of the main flywheel and collide with the side surface of the partition plate, the baffle plate is pushed to drive the auxiliary flywheel to rotate under continuous impact, so that power transmission is realized, and resonance between the main flywheel and the auxiliary flywheel is eliminated because no direct interaction force exists between the main flywheel and the auxiliary flywheel, therefore, the condition of violent vibration does not occur in the process from starting to normal running of the engine, and the smoothness is improved; in addition, because the main flywheel and the auxiliary flywheel are driven by oil, the two flywheels can rotate in 360 degrees in any direction, torsional vibration and rolling vibration at two ends are effectively isolated, even if external instant impact torque occurs, the main flywheel cannot lose the power of the whole vehicle due to the problem of the impact torque, the real flexible connection is realized, and the transmission smoothness is improved.
In the above-described hydraulic dual mass flywheel, the outlet of the oil injection passage is provided toward the sub flywheel in the rotational direction of the main flywheel. The outlet of the oil injection channel is arranged to enable the oil injection channel to face the tangential direction along the rotating direction of the main flywheel and the auxiliary flywheel, so that the speed of the ejected high-pressure machine oil is corresponding to the rotating tangential speed of the main flywheel and the speed direction of the ejection of the engine oil, the impulse of the engine oil is improved, the starting speed is higher, and smooth transmission of power is facilitated.
In the hydraulic dual-mass flywheel, an annular oil cavity extending along the circumferential direction is formed between the main flywheel and the auxiliary flywheel, an outlet of the oil injection channel is communicated with the annular oil cavity, the partition plate is located in the annular oil cavity, the main flywheel is further provided with an oil return channel, an outlet of the oil return channel can be communicated with an oil pump, and an inlet of the oil return channel is communicated with the annular oil cavity. Through set up the annular oil pocket between main flywheel and vice flywheel, make the baffle be located annular oil intracavity and set up oil return channel on main flywheel, oil spout passageway and oil return channel all communicate with the annular oil pocket, the machine oil liquid that erupts like this can be injectd in the annular oil pocket, because oil return channel's suction effect cooperatees with the directional injection of machine oil liquid, can form the class that lasts the flow along main flywheel rotation direction between the export of oil spout passageway like this and oil return channel's entry, form continuous impact to the baffle that lies in the class like this, further improve the boot speed of vice flywheel, make power transmission more smooth-going nature.
In the above hydraulic dual-mass flywheel, the plurality of the partition plates are sequentially arranged at intervals along the circumferential direction of the auxiliary flywheel. Through setting up a plurality of baffles, improve the effect time and the frequency of baffle and the oil liquid inrush current like this, make power take off more smooth-going.
In the hydraulic dual-mass flywheel, the shape of the partition plate is matched with the shape of the cross section of the annular oil cavity, the annular oil cavity is divided into a plurality of independent sub oil cavities by the partition plates, through holes communicated with the adjacent sub oil cavities are formed in the partition plates, and throttle valves capable of controlling the flow of the cross sections of the through holes are arranged in the through holes. The shape through setting up the baffle cooperatees with the cross-sectional shape of annular oil pocket, the outer fringe of a plurality of baffles seals and separates whole annular oil pocket for a plurality of independent oil pockets with the inside wall cooperation of annular oil pocket like this, set up the through-hole on the baffle, machine oil liquid can only flow in the through-hole like this, improve the flow resistance and increase the effect to the baffle, through setting up the choke valve, the cross-sectional area size of steerable through-hole like this, the pressure of regulation and control oil pocket avoids the too big part damage that causes of oil pressure.
In the above hydraulic dual-mass flywheel, the outlet position of the oil injection passage and the inlet position of the oil return passage are symmetrically arranged along the center of the main flywheel. The outlet position of the oil injection channel and the inlet position of the oil return channel are symmetrically arranged along the center, so that the two positions are ensured not to cause power transmission gear failure due to being located in the same oil cavity, and the smooth effect of power transmission is ensured.
In the above hydraulic dual-mass flywheel, the inner side wall of the through hole has a chute opened along the radial direction, the throttle valve includes a spring member and a plunger piston capable of moving along the chute, the spring member is located at the bottom of the chute and abuts against one end of the plunger piston, and the other end of the plunger piston is spherical and extends into the through hole. Through set up spring part and plunger in the spout to the one end that sets up the plunger and stretch into the through-hole is the sphere form and the other end leans on with the spring part top, when the pressure of machine fluid is great like this on the sphere of pressure effect to plunger tip, promote the plunger and retreat under the effect of pressure component, thereby improve the through-flow of through-hole, realize the effect of automatically regulated pressure release, thereby avoid the too big effort change that guarantees that the baffle receives of oil pressure at less within range, improve power transmission's ride comfort.
In the above hydraulic dual-mass flywheel, the plunger has a projection on its outer circumferential surface, the inner side wall of the chute has a step surface for limiting the sliding displacement of the projection, and a flow space is always provided between the other end of the plunger and the inner side wall of the through hole when the projection abuts against the step surface. Thereby can make the other end of plunger and the inside wall of through-hole have the circulation space all the time through set up the lug on the plunger and can make with the spacing cooperation of the step face of spout inside wall, like this the mobility of homoenergetic assurance machine fluid under any state to guarantee that flow resistance and baffle continuous action make power transmission smooth-going stable.
In the above hydraulic dual-mass flywheel, both the width dimension of the outlet of the oil injection channel along the circumferential direction of the main flywheel and the width dimension of the inlet of the oil return channel along the circumferential direction of the main flywheel are greater than the width dimension of the partition plate along the circumferential direction of the auxiliary flywheel. By setting the width dimension of the oil injection channel outlet along the circumferential direction of the main flywheel and the width dimension of the oil return channel inlet along the circumferential direction of the main flywheel to be larger than the width dimension of the partition plate along the circumferential direction of the auxiliary flywheel, the situation that when the oil injection channel outlet or the oil return channel inlet is just improved to be just right opposite to the partition plate, the partition plate is completely blocked, and the influence on power transmission caused by the fact that oil cannot be injected by the engine oil is avoided.
In the above-mentioned hydraulic dual-mass flywheel, an inlet of the oil return passage is opened toward the auxiliary flywheel along a rotation direction of the main flywheel, and an inlet of the oil return passage is disposed opposite to an outlet of the oil injection passage along a circumferential direction of the main flywheel. The inlet orientation through setting up oil return passage sets up towards vice flywheel along the tangential, and sets up along the circumference of main flywheel with the export orientation of oil spout passageway relatively, thereby for providing further direction along the machine oil liquid that main flywheel rotation direction flows, thereby the passageway speed of returning flow improves power transmission effect.
Compared with the prior art, the invention has the following advantages:
1. the hydraulic double-mass flywheel is communicated with an oil pump of an engine by arranging an oil injection channel on a main flywheel, so that high-pressure oil can be pumped out from the oil pump to enter the oil injection channel when the engine runs, then a partition plate is arranged on an auxiliary flywheel, the outlet of the oil injection channel faces the auxiliary flywheel, so that the high-pressure oil gushing out from the oil injection channel can be sprayed towards the auxiliary flywheel, the main flywheel rotates at a high speed relative to the auxiliary flywheel, so that the sprayed high-pressure oil can continue to move tangentially under the action of the inertia of the main flywheel and collide with the side surface of the partition plate, the partition plate is pushed under continuous impact to drive the auxiliary flywheel to rotate so as to realize power transmission, no direct interaction force exists between the main flywheel and the auxiliary flywheel, the resonance phenomenon between the main flywheel and the auxiliary flywheel in the existing structure is completely eliminated, and the engine can not generate severe vibration in the, the smoothness is improved.
2. According to the hydraulic dual-mass flywheel, due to the fact that the main flywheel and the auxiliary flywheel are driven through oil, the two flywheels can rotate in 360 degrees in any direction, torsional vibration and rolling vibration at two ends are effectively isolated, even though external instant impact torque occurs, the main flywheel cannot lose the power of the whole vehicle due to the impact torque, real flexible connection is achieved, and transmission smoothness is improved.
Drawings
Fig. 1 is a schematic perspective view of the hydraulic dual-mass flywheel.
Fig. 2 is a schematic sectional structure diagram of the hydraulic double-mass flywheel.
Fig. 3 is an enlarged view of a portion a in fig. 2.
Fig. 4 is a schematic cross-sectional structure diagram of the hydraulic double-mass flywheel at another angle.
Fig. 5 is an enlarged view of a portion B in fig. 4.
Fig. 6 is a schematic diagram of a partial explosion structure of the present hydraulic dual mass flywheel.
Fig. 7 is a perspective view of a partial structure of the sub flywheel.
In the figure, 1, a main flywheel; 11. an oil injection channel; 12. an oil return passage;
2. an auxiliary flywheel; 21. a partition plate; 211. a through hole; 212. a chute; 213. a step surface;
3. an annular oil chamber; 31. a sub-oil chamber;
4. a throttle valve; 41. a plunger; 411. a bump; 42. a spring member;
5. a flow-through space.
Detailed Description
The following are specific embodiments of the present invention and are further described with reference to the drawings, but the present invention is not limited to these embodiments.
As shown in fig. 1, 2, 6 and 7, the hydraulic dual-mass flywheel comprises a main flywheel 1 and an auxiliary flywheel 2 which are coaxially arranged and can rotate relatively, wherein an oil injection channel 11 with an inlet capable of being communicated with an oil pump is arranged in the main flywheel 1, an outlet of the oil injection channel 11 faces the auxiliary flywheel 2, a partition plate 21 extending along the radial direction is arranged on the auxiliary flywheel 2, and engine oil gushing out from the outlet of the oil injection channel 11 can be sprayed on the side surface of the partition plate 21 when the main flywheel 1 rotates relative to the auxiliary flywheel 2. The main flywheel 1 is used for being connected with a crankshaft and synchronously rotating, the main flywheel 1 stores energy and transmits the rotating torque of an engine when rotating, and the auxiliary flywheel 2 is used for being matched with a clutch and placed on one side of a transmission system so as to improve the rotating inertia of the transmission. The oil injection channel 11 is arranged on the main flywheel 1, the inlet of the nozzle channel can be communicated with the oil pump of the engine, so that high-pressure oil liquid can be pumped out from the oil pump to enter the oil injection channel 11 when the engine runs, the partition plate 21 is arranged on the auxiliary flywheel 2, the outlet of the oil injection channel 11 faces the auxiliary flywheel 2, so that the high-pressure oil liquid effusing from the oil injection channel 11 can be sprayed towards the auxiliary flywheel 2, the main flywheel 1 rotates at a high speed relative to the auxiliary flywheel 2, the sprayed high-pressure oil liquid can continue to move along the tangential direction under the inertia effect of the main flywheel 1 and collide with the side surface of the partition plate 21, the partition plate 21 is pushed to drive the auxiliary flywheel 2 to rotate under continuous impact, so that power transmission is realized, as the direct interaction force does not exist between the main flywheel 1 and the auxiliary flywheel 2, the resonance between the main flywheel 1 and the auxiliary flywheel 2 is eliminated, and the engine can not, the smoothness is improved; in addition, because the main flywheel 1 and the auxiliary flywheel 2 are driven by oil, the two flywheels can rotate in any direction by 360 degrees, torsional vibration and rolling vibration at two ends are effectively isolated, even if external instant impact torque occurs, the main flywheel 1 cannot lose the power of the whole vehicle due to the problem of the impact torque, the real flexible connection is realized, and the transmission smoothness is improved. Further, the outlet of the oil injection channel 11 is positioned on the side surface of the main flywheel 1 facing the auxiliary flywheel 2, and the outlet of the oil injection channel 11 is obliquely arranged along the tangential direction of rotation of the main flywheel 1. The outlet of the oil injection channel 11 is arranged on the side face, facing the auxiliary flywheel 2, of the main flywheel 1 and faces the tangential inclination along the rotating direction of the main flywheel 1, so that the speed of the ejected high-pressure machine oil is corresponding to the rotating tangential speed of the main flywheel 1 and the speed direction of the ejection of the engine oil, the impulse of the engine oil is increased, the starting speed is higher, and smooth transmission of power is facilitated. Preferably, the partition plates 21 are four and are sequentially and uniformly spaced along the circumferential direction of the auxiliary flywheel 2. By arranging the four partition plates 21, the acting time and frequency of the partition plates 21 and the oil liquid surge are improved, and the power output is smoother.
As shown in fig. 1-7, an annular oil chamber 3 extending along the circumferential direction is arranged between the main flywheel 1 and the auxiliary flywheel 2, an outlet of the oil injection channel 11 is communicated with the annular oil chamber 3, the partition plate 21 is positioned in the annular oil chamber 3, an oil return channel 12 with an outlet capable of being communicated with an oil pump is further arranged on the main flywheel 1, and an inlet of the oil return channel 12 is communicated with the annular oil chamber 3. Through set up annular oil pocket 3 between main flywheel 1 and vice flywheel 2, make baffle 21 be located annular oil pocket 3 and set up oil return passage 12 on main flywheel 1, oil spout passage 11 and oil return passage 12 all communicate with annular oil pocket 3, the machine oil liquid that erupts like this can be injectd in annular oil pocket 3, because the suction of oil return passage 12 cooperatees with the directional injection of machine oil liquid, can form the gush flow of following main flywheel 1 rotation direction and continuing the flow between the export of oil spout passage 11 and the entry of oil return passage 12 like this in annular oil pocket 3, form continuous impact to the baffle 21 that lies in the gush flow like this, further improve the boot-up speed of vice flywheel 2, make power transmission more smooth-going nature. The inlet of the oil return channel 12 is opened towards the auxiliary flywheel 2 along the tangential direction, and the inlet of the oil return channel 12 faces the opposite direction of the rotation direction of the main flywheel 1. The inlet of the oil return channel 12 is inclined towards the tangential direction and is opposite to the rotation direction of the main flywheel 1, so that further guidance is provided for engine oil flowing along the rotation direction of the main flywheel 1, and the return speed of the channel improves the power transmission effect. The outlet position of the oil injection channel 11 and the inlet position of the oil return channel 12 are symmetrically arranged along the center of the main flywheel 1 and are both arranged at the outer edge of the main flywheel 1. The outlet position of the oil injection channel 11 and the inlet position of the oil return channel 12 are arranged along the center symmetrically, so that the two positions are ensured not to cause power transmission gear failure due to being positioned in the same oil cavity 31, the smooth power transmission effect is ensured, the linear speed at the outer edge of the main flywheel 1 is the maximum, and the engine oil liquid impulse is improved. The shape of the partition plate 21 is matched with the shape of the cross section of the annular oil chamber 3, the annular oil chamber 3 is divided into four independent oil chambers 31 by the four partition plates 21, through holes 211 which are communicated with the adjacent oil chambers 31 are formed in the partition plates 21, and throttle valves 4 which can control the cross section flow of the through holes 211 are arranged in the through holes 211. Through the shape that sets up baffle 21 and the cross sectional shape of annular oil chamber 3 cooperate, like this the outer fringe of a plurality of baffles 21 seals with the inside wall cooperation of annular oil chamber 3 and separates whole annular oil chamber 3 for a plurality of independent seed oil chamber 31, set up through-hole 211 on baffle 21, machine oil liquid can only flow in through-hole 211 like this, improve the effect that the flow resistance increases baffle 21, through setting up choke valve 4, the cross sectional area size of steerable through-hole 211 like this, the pressure of regulation and control seed oil chamber 31, avoid the too big part damage that causes of oil pressure. The width dimension of the outlet of the oil injection channel 11 along the circumferential direction of the main flywheel 1 and the width dimension of the inlet of the oil return channel 12 along the circumferential direction of the main flywheel 1 are both larger than the width dimension of the partition plate 21 along the circumferential direction of the auxiliary flywheel 2. By setting the width dimension of the outlet of the oil injection channel 11 along the circumferential direction of the main flywheel 1 and the width dimension of the inlet of the oil return channel 12 along the circumferential direction of the main flywheel 1 to be larger than the width dimension of the partition plate 21 along the circumferential direction of the auxiliary flywheel 2, the situation that the mechanical oil cannot be injected to influence power transmission because the outlet of the oil injection channel 11 or the inlet of the oil return channel 12 is completely blocked by the partition plate 21 when the outlet of the oil injection channel 11 or the inlet of the oil return channel 12 is just right aligned.
As shown in fig. 4-7, the inner side wall of the through hole 211 has a sliding slot 212 opened along the radial direction, the throttle valve 4 includes a spring member 42 and a plunger 41 capable of moving along the sliding slot 212, the spring member 42 is a compression spring, the spring member 42 is located at the bottom of the sliding slot 212 and abuts against one end of the plunger 41, and the other end of the plunger 41 is spherical and extends into the through hole 211. Through set up spring part 42 and plunger 41 in spout 212 to set up plunger 41 and stretch into the one end of through-hole 211 and be the sphere and the other end and spring part 42 top lean on, when the pressure of machine oil liquid is great like this pressure effect to the sphere of plunger 41 tip, push plunger 41 and retreat under the pressure component effect, thereby improve the through-flow of through-hole 211, realize the effect of automatically regulated pressure release, thereby avoid the too big effort change that guarantees that baffle 21 received in less within range, improve the smoothness of power transmission. The plunger 41 has a projection 411 on the outer peripheral surface thereof, the slide groove 212 has a step surface 213 on the inner side wall thereof for restricting the sliding displacement of the projection 411, and a flow space 5 is always provided between the other end of the plunger 41 and the inner side wall of the through hole 211 when the projection 411 abuts against the step surface 213. Through set up lug 411 can be spacing with the step face 213 of the inside wall of spout 212 spacing cooperation thereby make the other end of plunger 41 and the inside wall of through-hole 211 have circulation space 5 all the time on plunger 41, like this under any state the mobility of the homoenergetic assurance machine fluid to guarantee that flow resistance and baffle 21 continue to act on and make power transmission smooth and stable. Specifically, the auxiliary flywheel 2 comprises four flange pieces which are spliced end to form a ring, combination plates are arranged at two ends of each arc-shaped flange piece, the combination plates of two adjacent flange pieces are abutted and connected to form a partition plate 21, and the combination plates are connected through bolts. This facilitates the installation of the throttle valve 4. The main flywheel 1 comprises a flywheel disc and an annular housing, the outer edge of the annular housing is connected with the outer peripheral face of the flywheel disc in a sealing mode, the inner edge of the annular housing is attached to the outer surface of the auxiliary flywheel 2 in a sealing mode, and an annular oil cavity 3 is formed among the annular housing, the flywheel disc and the auxiliary flywheel 2. This facilitates the mounting of the secondary flywheel 2 between the flywheel disc and the annular housing.
The specific embodiments described herein are merely illustrative of the spirit of the invention. Various modifications or additions may be made to the described embodiments or alternatives may be employed by those skilled in the art without departing from the spirit or ambit of the invention as defined in the appended claims.
Claims (9)
1. A hydraulic double-mass flywheel comprises a main flywheel (1) and an auxiliary flywheel (2) which are coaxially arranged and can rotate relatively, wherein an oil injection channel (11) with an inlet capable of being communicated with an oil pump is arranged in the main flywheel (1), an outlet of the oil injection channel (11) faces to the auxiliary flywheel (2), a partition plate (21) extending along the radial direction is arranged on the auxiliary flywheel (2), and when the main flywheel (1) rotates relative to the auxiliary flywheel (2), engine oil gushed from the outlet of the oil injection channel (11) can be sprayed on the side surface of the partition plate (21) and pushes the auxiliary flywheel (2) to rotate; an annular oil cavity (3) extending along the circumferential direction is formed between the main flywheel (1) and the auxiliary flywheel (2), an outlet of the oil injection channel (11) is communicated with the annular oil cavity (3), and the partition plate (21) is positioned in the annular oil cavity (3); the annular oil chamber (3) is divided into a plurality of independent sub-oil chambers (31) by a plurality of partition plates (21), and the partition plates (21) are provided with through holes (211) communicated with the adjacent sub-oil chambers (31), and the annular oil chamber is characterized in that throttle valves (4) capable of controlling the section flow of the through holes (211) are arranged in the through holes (211); the inner side wall of the through hole (211) is provided with a sliding groove (212) which is opened along the radial direction, the sliding groove (212) extends from the inner side wall of the through hole (211) to the inner side along the radial direction of the auxiliary flywheel (2), the throttle valve (4) comprises a spring piece (42) and a plunger (41) which can move along the sliding groove (212), the spring piece (42) is positioned at the bottom of the sliding groove (212) and is abutted against one end of the plunger (41), and the other end of the plunger (41) is spherical and extends into the through hole (211); and a flow space (5) is always arranged between the other end of the plunger (41) and the inner side wall of the through hole (211).
2. A hydrodynamic twin mass flywheel according to claim 1, characterized in that the outlet of the oil injection channel (11) is arranged in the direction of rotation of the main flywheel (1) towards the secondary flywheel (2).
3. A hydrodynamic twin mass flywheel according to claim 1 or 2, characterised in that the main flywheel (1) is also provided with an oil return channel (12) whose outlet can communicate with an oil pump, the inlet of the oil return channel (12) communicating with the annular oil chamber (3).
4. A hydrodynamic twin mass flywheel according to claim 1 or 2, characterized in that said partitions (21) are several and are arranged in succession at intervals in the circumferential direction of said secondary flywheel (2).
5. A hydrodynamic twin mass flywheel as defined in claim 3, characterized in that said bulkhead (21) has a shape adapted to the cross-sectional shape of said annular oil chamber (3).
6. A hydrodynamic twin mass flywheel according to claim 5, characterized in that the outlet position of the oil injection channel (11) and the inlet position of the oil return channel (12) are arranged symmetrically along the centre of the main flywheel (1).
7. A hydrodynamic twin mass flywheel according to claim 1, characterized in that the outer peripheral surface of the plunger (41) has a projection (411), the inner side wall of the runner (212) has a step surface (213) which limits the sliding displacement of the projection (411), and a flow space (5) is always provided between the other end of the plunger (41) and the inner side wall of the through hole (211) when the projection (411) abuts against the step surface (213).
8. A hydrodynamic twin mass flywheel according to claim 3, characterized in that the width dimension of the outlet of the oil injection channel (11) in the circumferential direction of the main flywheel (1) and the width dimension of the inlet of the oil return channel (12) in the circumferential direction of the main flywheel (1) are both greater than the width dimension of the partition (21) in the circumferential direction of the secondary flywheel (2).
9. A hydrodynamic twin mass flywheel according to claim 3, characterized in that the inlet of the oil return channel (12) opens in the direction of rotation of the main flywheel (1) towards the secondary flywheel (2), the inlet of the oil return channel (12) facing opposite the outlet of the oil injection channel (11) facing in the circumferential direction of the main flywheel (1).
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| CN2223791Y (en) * | 1995-05-18 | 1996-04-03 | 田丽敏 | Tempering and flow-rate control single-way valve |
| KR100535468B1 (en) * | 2003-09-09 | 2005-12-08 | 현대자동차주식회사 | Variable inertia fly wheel |
| CN103322121B (en) * | 2013-06-25 | 2015-11-18 | 长城汽车股份有限公司 | Double mass flywheel and the automobile with it |
| CN107504132B (en) * | 2017-05-18 | 2020-11-13 | 宝沃汽车（中国）有限公司 | Dual-mass flywheel and vehicle |
| CN109915540B (en) * | 2019-02-15 | 2020-08-18 | 宁波吉利罗佑发动机零部件有限公司 | Hydraulic vibration reduction dual-mass flywheel, oil way control system and automobile |
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2019
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