CN113983114B - Multi-inertia channel type power assembly hydraulic suspension with switchable states - Google Patents
Multi-inertia channel type power assembly hydraulic suspension with switchable states Download PDFInfo
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- CN113983114B CN113983114B CN202111426749.9A CN202111426749A CN113983114B CN 113983114 B CN113983114 B CN 113983114B CN 202111426749 A CN202111426749 A CN 202111426749A CN 113983114 B CN113983114 B CN 113983114B
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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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
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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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
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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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
- F16F13/107—Passage design between working chambers
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
The application discloses many inertia passageway formula power assembly hydraulic suspension of state switchable includes shell, vibration isolation mechanism, first valve and second valve. A cavity is arranged in the shell, and liquid is contained in the cavity; the vibration isolation mechanism is arranged in the cavity and divides the cavity into an upper cavity and a lower cavity; the vibration isolation mechanism is provided with a first inertia channel and a second inertia channel; the first valve is positioned at the inlet of the first inertia passage, and the second valve is positioned at the inlet of the second inertia passage; the first valve and the second valve can be opened or closed according to the pressure difference between the upper chamber and the lower chamber, so that the upper chamber is communicated with the lower chamber through the first inertia passage and/or the second inertia passage. Therefore, under different working conditions, the pressure difference between the upper chamber and the lower chamber is different, so that the first valve and/or the second valve are selectively opened or closed, different lag angle peak frequencies are obtained, the transmission of the vibration of the power assembly can be reduced in multiple frequency bands, and the vibration reduction effect is improved.
Description
Technical Field
The application relates to the technical field of automobiles, in particular to a multi-inertia channel type power assembly hydraulic suspension with switchable states.
Background
The hydraulic suspension of the automobile engine is an elastic connection system between an engine power assembly and a frame, and the design advantages and disadvantages of the damping performance of the system are directly related to the transmission of engine Vibration to an automobile body, so that the NVH (Noise, vibration and sound Vibration roughness, noise, vibration and Harshness) performance of the whole automobile is influenced. The common rubber suspension developed at first is widely applied due to low price and simple structure. However, the dynamic characteristics of the rubber suspension elements have two disadvantages: firstly, the vibration damping is small, and the requirements of the vibration isolation and vibration damping performance of a vehicle power assembly suspension system in a low frequency domain cannot be met; and secondly, a dynamic hardening phenomenon can occur during high-frequency vibration, so that the dynamic stiffness of the suspension system is obviously increased, the requirements on the vibration isolation and noise reduction performance of the suspension system of the automobile power assembly in a high-frequency domain cannot be met, and the later developed hydraulic suspension has better vibration isolation capability. The existing hydraulic suspension mainly comprises a simple throttling hole type, an inertia channel-decoupling film type and the like. However, the existing hydraulic mount has the following disadvantages: the existing hydraulic mount usually has good vibration damping effect only in a certain frequency range, and cannot meet the vibration damping requirement in the whole working range of an automobile. The newly proposed semi-active magnetic rheological fluid hydraulic mount and the active control type hydraulic mount have good vibration isolation and damping performance, but most of the semi-active magnetic rheological fluid hydraulic mount and the active control type hydraulic mount have complex structures and high cost and are not widely applied. In addition, structures such as an electromagnetic valve and a motor are also needed to be added to some semi-active control hydraulic suspensions, so that the cost and the implementation difficulty are increased.
In the single inertia path type hydraulic mount of a general structure, the frequency of occurrence of a peak value of a lag angle is usually in a range of 7 to 15Hz in order to attenuate the vibration of the powertrain caused by the excitation of the road surface or the fluctuation of the output torque of the powertrain. In the design of hydraulic mount, the shape of main rubber spring and the hardness of rubber material are usually designed to satisfy its static characteristics, and the adjustment of the peak frequency of the lag angle is usually achieved by changing the size of inertia channel. Due to structural limitations, it is often difficult to achieve the desired peak frequency of the lag angle by adjusting the size of the inertia track alone. On the other hand, the excitation dominant frequency of the engine is twice the crankshaft rotation frequency, which can be calculated by the following formula:
in the formula, n is the engine crankshaft speed, and j is the number of cylinders of the engine. For a four cylinder engine, when the engine is idling at 710r/min, the dominant frequency of the vibration excitation at idle can be determined by the above equation to be 23.7Hz. In order to reduce the vibration of the steering wheel, the gear lever and other systems caused by the excitation of the engine, the suspension system is expected to have smaller rigidity near the idle speed of the engine, and in this case, the hydraulic suspension is required to have larger lag angle peak frequency (above 20 Hz), and the high lag angle peak frequency is difficult to achieve by adjusting the size of the single inertia channel.
Disclosure of Invention
One of the purposes of the present application is to provide a new technical solution of a multi-inertia channel type power assembly hydraulic mount with switchable states, which sets a double-inertia channel through adjustment, and controls the opening and closing of the double-inertia channel under different working conditions to adjust the influence of engine vibration on the automobile.
According to a first aspect of the application, a state-switchable multi-inertia channel powertrain hydraulic mount is provided, comprising: a housing, a vibration isolation mechanism, a first valve, and a second valve. A cavity is arranged in the shell, and liquid is contained in the cavity; the vibration isolation mechanism is arranged in the cavity and divides the cavity into an upper cavity and a lower cavity; a first inertia channel and a second inertia channel are arranged on the vibration isolation mechanism; the first inertia channel and the second inertia channel are both used for communicating the upper chamber and the lower chamber; the first valve is located at an inlet of the first inertia track, and the second valve is located at an inlet of the second inertia track; the first valve and the second valve can be opened or closed according to the pressure difference between the upper chamber and the lower chamber, so that the upper chamber and the lower chamber are communicated through the first inertia passage and/or the second inertia passage.
In one embodiment, the first valve comprises a first shell, a first moving plate, a first guide rod, a first inner spring and a first outer spring which are coaxially arranged, the first shell is provided with a first accommodating chamber, the first accommodating chamber comprises a first closed cavity and a first avoiding cavity which are sequentially distributed from top to bottom, and the inner diameter of the first avoiding cavity is larger than that of the first closed cavity; the outer diameter of the first movable disc is the same as the inner diameter of the first closed cavity; the first guide rod is partially positioned in the first accommodating chamber and partially positioned outside the first accommodating chamber, a first upper limiting block is arranged on the part of the first guide rod positioned outside the first accommodating chamber, a lower limiting block is arranged on the part of the first guide rod positioned inside the first accommodating chamber, and the lower edge of the lower limiting block is aligned with the lower edge of the first avoiding cavity; the first movable disc is sleeved on the part of the first guide rod between the first upper limiting block and the lower limiting block and can move between the first upper limiting block and the lower limiting block along the first guide rod; the first inner spring is sleeved on the first guide rod, one end of the first inner spring is fixedly connected with the bottom of the first movable disc, the other end of the first inner spring is abutted to the bottom wall of the first containing chamber, the first outer spring is sleeved on the first guide rod, the bottom end of the first outer spring is abutted to the bottom wall of the first containing chamber, and the distance between the top end of the first outer spring and the lower surface of the first upper limiting block is larger than the thickness of the first movable disc under the condition that an engine is not started.
In one embodiment, the second valve comprises a second housing, a second movable disk, a second guide rod, a second inner spring and a second outer spring which are coaxially arranged, the second housing is provided with a second containing chamber, the second containing chamber comprises a second upper sealing cavity, a second avoiding cavity and a second lower sealing cavity which are sequentially distributed from top to bottom, the inner diameter of the second avoiding cavity is larger than the inner diameters of the second upper sealing cavity and the second lower sealing cavity, and the outer diameter of the second movable disk is equal to the inner diameters of the second upper sealing cavity and the second lower sealing cavity; the second guide rod is positioned in the second accommodating chamber, one end of the second guide rod is connected with a second upper limiting block, and the lower edge of the second upper limiting block is aligned with the opening of the second accommodating chamber; the second movable disc is sleeved on the second guide rod and can move up and down along the second guide rod; the second inner spring is sleeved on the second guide rod, one end of the second inner spring is fixedly connected with the bottom of the second movable plate, the other end of the second inner spring is abutted to the bottom wall of the second containing chamber, the second outer spring is sleeved on the second guide rod, the bottom end of the second outer spring is abutted to the bottom wall of the second containing chamber, and the distance between the top end of the second outer spring and the lower surface of the second upper limiting block is larger than the thickness of the second movable plate when an engine is not started.
In one embodiment, the vibration isolation mechanism comprises an upper runner plate, a lower runner plate and a decoupling film, wherein the upper runner plate and the lower runner plate are attached and fixedly embedded on the inner wall of the cavity to divide the cavity into an upper cavity type and a lower cavity, through holes are formed in the middle parts of the upper runner plate and the lower runner plate, part of the decoupling film is fixedly embedded in the through holes formed in the upper runner plate, the other part of the decoupling film is embedded in the through holes formed in the lower runner plate, the upper runner plate forms the bottom wall of the upper cavity, and the lower runner plate forms the top wall of the lower cavity; the upper flow field plate and the lower flow field plate cooperate to form the first inertial channel and the second inertial channel.
In one embodiment, two C-shaped grooves are formed in one side of the lower runner plate, which is close to the upper runner plate, and the C-shaped openings of the two grooves are oppositely arranged; the upper runner plate is provided with two openings, one of the openings is communicated with one end of the groove to form the first inertia channel; wherein another of said openings communicates with another of said recesses to form said second inertia track.
In one embodiment, a flexible membrane is arranged in the lower cavity and divides the lower cavity into a liquid chamber and an air chamber which are distributed up and down.
In one embodiment, the housing is provided with a vent hole communicating with the air chamber.
In one embodiment, the flexible membrane is a rubber membrane.
In one embodiment, the housing includes an upper shell and a lower shell, the upper shell being removably coupled to the lower shell to form the housing.
In one embodiment, the upper shell is provided with a rubber main spring and a reinforcing block.
The application provides a multi-inertia channel type power assembly hydraulic suspension with switchable states, which comprises a shell, a vibration isolation mechanism, a first valve and a second valve. A cavity is arranged in the shell, and liquid is contained in the cavity; the vibration isolation mechanism is arranged in the cavity and divides the cavity into an upper cavity and a lower cavity; a first inertia channel and a second inertia channel are arranged on the vibration isolation mechanism; the first inertia channel and the second inertia channel are both used for communicating the upper chamber and the lower chamber; the first valve is positioned at the inlet of the first inertia passage, and the second valve is positioned at the inlet of the second inertia passage; the first valve and the second valve can be opened or closed according to the pressure difference between the upper chamber and the lower chamber, so that the upper chamber and the lower chamber are communicated through the first inertia passage and/or the second inertia passage. In this application, set up first inertia passageway and second inertia passageway on the one hand at the vibration isolation mechanism, adopt two inertia passageways, increased the damping coefficient of liquid, improved hydraulic mount's the ability of absorbing, increased the effect of absorbing. The first valve and the second valve are respectively arranged at the inlets of the first inertia channel and the second inertia channel, so that the pressure difference of the upper chamber and the lower chamber is different under different working conditions of the automobile, the first valve and/or the second valve is/are selectively opened or closed, different peak values of the lag angle are obtained, the transmission of the vibration of the power assembly can be reduced in multiple frequency bands, and the vibration reduction effect is improved.
Further features of the present application and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which is to be read in connection with the accompanying drawings.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the application and together with the description, serve to explain the principles of the application.
Fig. 1 is a general structural sectional view of a state-switchable multi-inertia-channel power assembly hydraulic suspension provided by an embodiment of the application.
FIG. 2 is a schematic view of a first inertial channel and a second inertial channel.
FIG. 3 is a schematic view of the first valve in an intermediate closed state.
Fig. 4 is a schematic view of the first valve in the open state.
Fig. 5 is a schematic view of the first valve in an open state.
Fig. 6 is a schematic view of the second valve in an intermediate open state.
Fig. 7 is a schematic diagram of variation of simulated dynamic stiffness with frequency in different opening states of the first inertial channel and the second inertial channel.
Fig. 8 is a schematic diagram illustrating a variation of the simulated lag angle with frequency in different opening states of the first inertia passage and the second inertia passage.
The figures are labeled as follows: 1-an upper shell, 2-a lower shell, 3-a first valve, 3 a-a first shell, 4-a lower runner plate, 5-an upper runner plate, 6-a rubber main spring, 7-an upper connecting bolt, 8-a reinforcing block, 9-a lower connecting bolt, 10-a vent hole, 11-a flexible membrane, 12-an upper chamber, 13-a lower chamber, 14-a first outlet, 15-a first opening, 16-a first inlet, 17-a sealing ring, 18-a decoupling membrane, 19-a first inertial channel, 20-a second inertial channel, 21-a second inlet, 22-a first movable disk, 23-a first guide rod, 23 a-a first upper limiting block, 23 b-a lower limiting block, 24-a first outer spring, 25-a first inner spring, 26-a first avoiding cavity, 26 a-a first closed cavity, 27-a second shell, 27-a second outer spring, 29-a second inner spring, 30-a second upper limiting block, 31-a second closed cavity, 32-a second lower limiting cavity.
Detailed Description
Various exemplary embodiments of the present application will now be described in detail with reference to the accompanying drawings. It should be noted that: the relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present application unless specifically stated otherwise.
The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the application, its application, or uses.
Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.
In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values.
As shown in fig. 1 and 2, the multi-inertia channel type power assembly hydraulic suspension with switchable states provided by the embodiment of the application comprises a shell, an isolation mechanism, a first valve 3 and a second valve 27. A cavity is arranged in the shell, and liquid is contained in the cavity; the vibration isolation mechanism is arranged in the cavity and divides the cavity into an upper cavity chamber 12 and a lower cavity chamber 13; a first inertia channel 19 and a second inertia channel 20 are arranged on the vibration isolation mechanism; the first inertia passage 19 and the second inertia passage 20 are both used for communicating the upper chamber 12 and the lower chamber 13; the first valve 3 is located at the inlet of the first inertia track 19 and the second valve 27 is located at the inlet of the second inertia track 20; both the first valve 3 and the second valve 27 can be opened or closed according to the pressure difference between the upper chamber 12 and the lower chamber 13, so that the upper chamber 12 and the lower chamber 13 communicate through the first inertia track 19 and/or the second inertia track 20. As will be appreciated by those skilled in the art, the liquid may be a liquid with relatively good flow stability, such as glycol, to ensure that the liquid can reliably and stably flow in the inertia track when subjected to the vibration exciting force.
In the embodiment of the application, on one hand, the first inertia channel 19 and the second inertia channel 20 are arranged on the vibration isolation mechanism, and two inertia channels are adopted, so that the damping coefficient of liquid is increased, the vibration absorption capacity of the hydraulic suspension is improved, and the vibration absorption effect is improved. In another aspect of the embodiment of the present invention, the first valve 3 and the second valve 27 are respectively disposed at the inlets of the first inertia passage 19 and the second inertia passage 20, so that the pressure difference between the upper chamber 12 and the lower chamber 13 is different under different operating conditions of the vehicle, and the first valve 3 and/or the second valve 27 are/is selectively opened or closed, thereby obtaining different peak frequencies of the lag angle, and thus reducing the transmission of the powertrain vibration in multiple frequency bands and increasing the damping effect.
In one embodiment, the first valve 3 includes a first housing 3a, a first moving disk 22, a first guide rod 23, a coaxially disposed first inner spring 25 and a first outer spring 24. The first shell 3a is provided with a first accommodating chamber, the first accommodating chamber comprises a first closed cavity 26a and a first avoiding cavity 26 which are sequentially distributed from top to bottom, and the inner diameter of the first avoiding cavity 26 is larger than that of the first closed cavity 26 a; the outer diameter of the first moving disk 22 is the same as the inner diameter of the first closing chamber 26 a. It will be appreciated by those skilled in the art that the first movable disk 22 is circumferentially provided with a sealing layer, which may be embodied as a layer of sealing rubber gasket or the like. The first guide rod 23 is partially positioned in the first accommodating chamber and partially positioned outside the first accommodating chamber, a first upper limiting block 23a is arranged on the part of the first guide rod 23 positioned outside the first accommodating chamber, a lower limiting block 23b is arranged on the part positioned inside the first accommodating chamber, and the lower edge of the lower limiting block 23b is aligned with the lower edge of the first avoiding cavity 26; the first movable tray 22 is sleeved on a portion of the first guide rod 23 between the first upper limit block 23a and the lower limit block 23b, and is movable between the first upper limit block 23a and the lower limit block 23b along the first guide rod 23. In this embodiment, the first upper and lower stoppers 23a and 23b are made of a rubber material to reduce impact noise between the first moving plate 22 and the first upper and lower stoppers 23a and 23 b.
As will be understood by those skilled in the art, during the movement of the first moving plate 22 from the first upper stopper 23a to the lower stopper 23b along the first guide bar 23, the first valve 3 is in an upper open state, a middle closed state, and a lower open state in this order. Specifically, with the first mobile disc 22 located between the first closing chamber 26a and the first upper limit block 23a, the first valve 3 is in the upper open state, as shown in fig. 3, in which the liquid can flow between the upper chamber 12 and the lower chamber 13 through the first inertia track 19; with at least part of the first mobile disc 22 in the first closing chamber 26a, the first valve 3 is in an intermediate closed condition, as shown in fig. 4, in which liquid cannot flow between the upper chamber 12 and the lower chamber 13 through the first inertia track 19; with the first moving disk 22 located between the first closing chamber 26a and the lower stopper 23b, i.e., with the first moving disk 22 located entirely in the evacuation chamber, the first valve 3 is in a lower open state, as shown in fig. 5, at which time liquid can flow between the upper chamber 12 and the lower chamber 13 through the first inertia track 19.
The first inner spring 25 is sleeved on the first guide rod 23, one end of the first inner spring 25 is fixedly connected with the bottom of the first movable plate 22, the other end of the first inner spring 25 is abutted to the bottom wall of the first accommodating chamber, the first outer spring 24 is sleeved on the first guide rod 23, the bottom end of the first outer spring 24 is abutted to the bottom wall of the first accommodating chamber, and the distance between the top end of the first outer spring 24 and the lower surface of the first upper limiting block 23a is larger than the thickness of the first movable plate 22 in the engine non-starting state. In the embodiment of the present application, the first outer spring 24 and the first inner spring 25 are provided so that the first moving plate 22 can be moved upward by an elastic force different from that to be overcome when it is moved downward. Specifically, since there is no fixed connection between the first outer spring 24 and the first movable plate 22, in the case that the first movable plate 22 moves upward beyond the natural length of the first outer spring 24, the first movable plate 22 is only acted by the elastic force of the first inner spring 25; after the first movable plate 22 moves downward to contact the first outer spring 24, the elastic force of the first outer spring 24 and the first inner spring 25 needs to be overcome during the downward movement. Specifically, in the present embodiment, the lengths of the first outer spring 24 and the first inner spring 25 satisfy the following requirements: when the engine is not started, the lower surface of the first movable disk 22 is in contact with the top end of the first outer spring 24, and the upper surface of the first movable disk 22 is flush with the upper end of the first upper closed chamber, i.e. when the first valve 3 is in an intermediate closed state. Thus, when the first movable tray 22 is in the upward open state, only the elastic force of the first inner spring 25 is applied, and the first inner spring 25 is in a stretched state; in the case where the first moving plate 22 is in the lower open state, the first outer spring 24 and the first inner spring 25 are applied with elastic force, and both the first outer spring 24 and the first inner spring 25 are in a compressed state.
In the embodiment of the application, when the engine works, the vibration excitation which is up and down reciprocated is transmitted to the suspension, specifically, when the vibration excitation which is down and is transmitted to the suspension through the upper connecting bolt 7, the upper connecting bolt compresses the rubber main spring 6 downwards, the volume of the upper chamber 12 is forced to be reduced, so that the pressure of the upper chamber 12 is increased, the liquid flows to the lower chamber 13 from the upper chamber 12 through the first inertia channel and/or the second inertia channel, the liquid in the lower chamber 13 is continuously increased, and the flexible membrane 11 at the bottom end of the lower chamber 13 has certain flexibility, and can expand to a certain degree so as to accommodate the increased liquid in the lower chamber. The pressure in the upper chamber 12 is greater than the pressure in the lower chamber 13 during this process.
Under the circumstances that the vibration rebounded upwards, the engine drove connecting bolt 7 and moved upwards for the volume of last chamber 12 constantly increases, and lower chamber 13 is at the in-process that the flexible membrane inflation state resumes, and the volume constantly reduces, and flexible membrane 11 resumes from the inflation state this moment, mainly resumes under the atmospheric pressure effect, and the compression rebound pumping action of similar piston cylinder, liquid flowed to upper chamber 12 through first inertia passageway and/or second inertia passageway from lower chamber 13 this moment. The pressure in the lower chamber 13 is greater than the pressure in the upper chamber 12 during this process.
Because the lower chamber is provided with the flexible membrane which has the deformation capability, the pressure in the lower chamber has little difference in the process that liquid flows from the upper chamber to the lower chamber or liquid flows from the lower chamber to the upper chamber, and the pressure in the upper chamber is mainly changed. Therefore, the pressure valve opens more downwardly than upwardly.
Generally, when the lower opening is started, the elastic coefficient of the spring is slightly larger due to larger pressure of the liquid; in the upper opening, the spring constant of the spring is set to be slightly smaller because the liquid pressure is smaller.
The elastic coefficient of one spring is constant and cannot be changed, so that the elastic coefficient of the spring can be specifically set according to the actual liquid pressure condition by arranging two springs, namely an outer spring and an inner spring, and setting that the elastic force of the two springs needs to be overcome when the valve is opened downwards and the elastic force of the inner spring needs to be overcome when the valve is opened upwards, so that the pressure for opening the pressure valve downwards is ensured to be larger than the pressure for opening the pressure valve upwards.
Specifically, in this embodiment, the first valve is provided with a first inner spring and a first outer spring, and the first valve needs to overcome the elastic forces of the first inner spring and the first outer spring during the lower opening process, and only needs to overcome the elastic force of the first inner spring during the upper opening process. The second valve is set the same as the first valve, and is not described again.
In one embodiment, the second valve 27 includes a second housing 27a, a second movable disk 32, a second guide rod, a second inner spring 29 and a second outer spring 28, which are coaxially disposed, the second housing 27a is provided with a second accommodating chamber, the second accommodating chamber includes a second upper sealing cavity 31, a second avoiding cavity 31a and a second lower sealing cavity 31b, which are sequentially distributed from top to bottom, an inner diameter of the second avoiding cavity 31a is greater than inner diameters of the second upper sealing cavity 31 and the second lower sealing cavity 31b, and an outer diameter of the second movable disk 32 is equal to inner diameters of the second upper sealing cavity 31 and the second lower sealing cavity 31 b. It will be appreciated by those skilled in the art that the second movable disk 32 is circumferentially provided with a sealing layer, which may be embodied as a layer of sealing rubber gasket or the like. The second guide rod is positioned in the second accommodating chamber, one end of the second guide rod is connected with a second upper limiting block 30, and the lower edge of the second upper limiting block 30 is aligned with the opening of the second accommodating chamber; the second movable plate 32 is sleeved on the second guide rod and can move up and down along the second guide rod. In this embodiment, the second upper limiting block 30 is made of rubber material to reduce the noise when the second moving plate 32 and the second upper limiting block 30 impact.
It will be understood by those skilled in the art that the second valve 27 is in the upper closed state, the intermediate open state and the lower closed state in sequence during the downward movement of the second moving plate 32 from the second upper stopper 30 along the second guide rod. Specifically, as shown in fig. 6, in the condition in which the second moving disk 32 is at least partially located in the second upper closed chamber 31, the second valve 27 is in the upper closed state, in which the liquid cannot circulate between the upper chamber 12 and the lower chamber 13 through the second inertia track 20; when the second movable disk 32 is fully located in the second escape chamber 31a, the second valve 27 is in an intermediate open state, and at this time, the liquid can circulate between the upper chamber 12 and the lower chamber 13 through the second inertia track 20; in the case where the second movable disk 32 is at least partially located in the second lower closing chamber 31b, the second valve 27 is in the lower closing state, in which the liquid cannot circulate between the upper chamber 12 and the lower chamber 13 through the second inertia track 20.
The second inner spring 29 is sleeved on the second guide rod, one end of the second inner spring 29 is fixedly connected with the bottom of the second movable plate 32, the other end of the second inner spring 29 is abutted to the bottom wall of the second containing chamber, the second outer spring 28 is sleeved on the second guide rod, the bottom end of the second outer spring 28 is abutted to the bottom wall of the second containing chamber, and in the state that an engine is not started, the distance between the top end of the second outer spring 28 and the lower surface of the second upper limiting block 30 is larger than the thickness of the second movable plate 32. In this embodiment, the arrangement and the purpose of the second outer spring 28 and the second inner spring 29 in the second valve 27 are the same as those of the first outer spring 24 and the first inner spring 25 in the first valve 3, and are not described herein again. In the present embodiment, the lengths of the second inner spring 29 and the second outer spring 28 are such that the second movable disk 32 is entirely located in the second escape chamber 31a when the engine is not started, i.e., the second valve 27 is in the intermediate open state. As such, in the case where the second valve 27 is in the upper-closed state, the second moving plate 32 is subjected to only the elastic force of the second inner spring 29, and the second inner spring 29 is in a stretched state; in the case where the second valve 27 is in the lower closed state, the second moving plate 32 is simultaneously subjected to the elastic forces of the second outer spring 28 and the second inner spring 29, and both the second outer spring 28 and the second inner spring 29 are in the compressed state.
It will also be understood by those skilled in the art that in the switchable multi-inertia track powertrain hydraulic mount provided in this embodiment, the first and second valves 3 and 27 are exposed to the same pressure applied to the upper and lower chambers 12 and 13. Therefore, in the case where the pressure in the upper chamber 12 is greater than the pressure in the lower chamber 13, the direction of the resultant pressure force of the upper chamber 12 and the lower chamber 13 is directed downward, and therefore, the first valve 3 has a tendency to switch from the intermediate closed state to the downward open state, and the pressure threshold value at which the first valve 3 is shifted from the intermediate closed state to the downward open state is set to P1; since the force received by the second movable disk 32 is the same as the resultant force of the pressure received by the first movable disk 22, the second valve 27 has a tendency to transition from the intermediate open state to the downward closed state, and the pressure threshold at which the second valve 27 transitions from the intermediate open state to the downward closed state is set to P2. In the case that the pressure of the lower chamber 13 is greater than the pressure of the upper chamber 12, the resultant force of the pressures of the upper chamber 12 and the lower chamber 13, which are applied to the first movable disk 22, is upward, so that the first valve 3 has a tendency to transition from the intermediate closed state to the upward open state, and the transition threshold value of the first valve 3 from the intermediate closed state to the upward open state is set to P1'; also, the force received by the second moving plate 32 is the same as the resultant force of the pressure received by the first moving plate 22, and therefore, the second valve 27 has a tendency to switch from the intermediate open state to the closed state, and the pressure threshold value at which the second valve 27 has a switch from the intermediate open state to the closed state is set to P2'. It will be understood by those skilled in the art that the first valve 3 and the second valve 27 can satisfy the following relationship by setting the spring constants of the first outer spring 24, the first inner spring 25, the second outer spring 28, and the second inner spring 29: p1 < P2, P1 '< P2'. For example, one way of setting may be to set the spring constant of the first inner spring 25 to be smaller than the spring constant of the second inner spring 29, and the spring constant of the first outer spring 24 to be smaller than the spring constant of the second outer spring 28. Of course, the skilled person can also arrange in other ways.
In one embodiment, the vibration isolation mechanism comprises an upper runner plate 5, a lower runner plate 4 and a decoupling film 18, wherein the upper runner plate 5 and the lower runner plate 4 are attached to each other and fixedly embedded on the inner wall of the cavity to divide the cavity into an upper cavity 12 and a lower cavity 13, through holes are formed in the middle parts of the upper runner plate 5 and the lower runner plate 4, part of the decoupling film 18 is fixedly embedded in the through holes formed in the upper runner plate 5, the other part of the decoupling film is embedded in the through holes formed in the lower runner plate 4, the upper runner plate 5 forms the bottom wall of the upper cavity 12, and the lower runner plate 4 forms the top wall of the lower cavity 13; the upper flow field plate 5 and the lower flow field plate 4 cooperate to form the first inertia track 19 and the second inertia track 20. In the embodiment, a decoupling film is also embedded between the upper runner plate and the lower runner plate, so that when liquid reaches the decoupling film through a through hole formed in the middle of the upper runner plate, the decoupling film only moves up and down in a free stroke under the condition that the suspension is excited by high frequency and small amplitude, no liquid flows in an inertial channel, and the inertial channel is in a dynamic hardening state; for the decoupling film type hydraulic suspension, the rigidity of the decoupling film is very low in small displacement, at the moment, the liquid between the upper cavity and the lower cavity only flows along with the deformation of the decoupling film, and no liquid flows in the inertia channel. Because the volume change of the upper and lower chambers is small when the amplitude is small, the volume change can be counteracted by the decoupling membrane deformation.
In one embodiment, two C-shaped grooves are formed on one side of the lower runner plate 4 close to the upper runner plate 5, and the C-shaped openings of the two grooves are oppositely arranged; the upper runner plate 5 is provided with two openings, one of the openings is communicated with one end of the groove to form the first inertia channel 19; the other of said openings communicating with the other of said recesses to form said second inertia track 20. Both grooves are formed along the outermost side of the lower flow channel plate 4, i.e. the side close to the side wall of the cavity, so that the length of the grooves can be increased to the greatest extent to increase the length of the first inertia channel 19 and the second inertia channel 20, thereby increasing the flow distance of the liquid and increasing the vibration damping effect. Of course, the grooves may have other distribution forms, but generally, two grooves extend along the circumferential direction of the lower flow channel plate 4, and two grooves are sequentially distributed along the circumferential direction of the lower flow channel plate 4, and the two grooves are not communicated with each other, and it will be understood by those skilled in the art that the cross section of the groove may be semicircular, square or V-shaped, and the cross section is preferably semicircular in this embodiment.
The lower flow channel plate 4 is further provided with a first inlet 16 and a first outlet 14 which are communicated with two ends of the first inertia channel 19, and is further provided with a first opening 15 which is coaxially communicated with the first outlet 14, when the first valve 3 is opened, the first inlet 16 is communicated with the upper chamber, liquid enters the first inertia channel 19 through the first inlet 16 and then flows to the first opening 15 from the first outlet 14, the first opening 15 is communicated with the lower chamber 13 or flows reversely, and finally the liquid can flow between the upper chamber and the lower chamber. Correspondingly, the lower flow channel plate 4 is further provided with a second inlet 21 and a second outlet which are communicated with two ends of the second inertia channel 20, and is further provided with a second opening which is coaxially communicated with the second outlet, when the second valve is opened, the second inlet is communicated with the upper chamber, liquid enters the second inertia channel 20 through the second inlet and flows to the second opening from the second outlet, the second opening is communicated with the lower chamber or flows in a reverse direction, and finally the liquid can flow between the upper chamber and the lower chamber.
It will also be appreciated by those skilled in the art that first inertial channel 19 and second inertial channel 20 may or may not be equal in length. In the present embodiment, the first inertial channel 19 and the second inertial channel 20 are preferably equal in length.
In one embodiment, a flexible membrane 11 is disposed in the lower chamber 13, and the flexible membrane 11 divides the lower chamber 13 into a liquid chamber and an air chamber which are distributed up and down. The flexible membrane 11 is convenient for forming a liquid chamber, and the vibration generated when the power assembly works is attenuated by further utilizing the elastic deformation characteristic of the flexible membrane 11, so that the influence of the vibration of the power assembly is reduced, and the noise transmitted to a passenger compartment is isolated.
In one embodiment, the flexible membrane 11 is a rubber membrane. The rubber membrane has the advantages of simple processing, low cost and durability.
In one embodiment, the housing comprises an upper shell 1 and a lower shell 2, and the upper shell 1 and the lower shell 2 are detachably connected to form the housing. It will be understood by those skilled in the art that a sealing ring 17 is further disposed between the upper casing 1 and the lower casing 2 to improve the sealing effect and prevent liquid leakage.
In one embodiment, the housing is provided with a vent 10 communicating with the air chamber, and in particular, the vent 10 is provided in the bottom wall of the lower case 2 so as to balance the air pressure, so that the flexible membrane 11 can be freely deformed. In one embodiment, the upper housing 1 is provided with a main rubber spring 6 and a reinforcing block 8. Specifically, one end of the rubber main spring 6 is fixedly connected with the upper shell 1, the other end of the rubber main spring is fixedly connected with the reinforcing block 8, and the rubber main spring 6 is fixed with the upper shell 1 and the reinforcing block 8 through a vulcanization process. The main rubber spring 6 is made of elastic rubber and plays a role in supporting the power assembly and providing friction damping, so that the vibration of the engine can be buffered, and the vibration of the engine can be reduced. And through the vulcanization process, the upper shell 1, the rubber main spring 6 and the reinforcing block 8 can form a whole, so that the service life of the suspension is prolonged.
In one embodiment, an upper connecting bolt 7 is fixed above the reinforcing block 8, and a lower connecting bolt 9 is fixed below the lower shell 2. The multi-inertia channel type power assembly hydraulic suspension with the switchable states is installed through the upper connecting bolt 7 and the lower connecting bolt 9, and is convenient and simple.
The following will specifically describe the opening conditions of the first inertia passage 19 and the second inertia passage 20 and the influence on the vibration under various working conditions of the multi-inertia passage type powertrain hydraulic suspension with switchable states provided by the embodiment of the present application.
First, as shown in fig. 7 and 8, simulation analysis is performed on the influence on the suspension dynamic characteristic when the first inertia path 19 and the second inertia path 20 are both opened and only the first inertia path 19 is opened by simulating simulation software, such as MATLAB software manufactured by MathWorks corporation, usa, and it can be understood by those skilled in the art that in the embodiment of the present application, the dynamic stiffness characteristic of the first inertia path and the second inertia path are the same, and therefore, when the first inertia path or the second inertia path is opened alone, the influence on the suspension dynamic characteristic is the same. From the figure, it can be seen that as the number of inertia track openings increases, the peak value of the angle of lag and the frequency of the peak value of the angle of lag of the mount increase. When only the first inertia channel 19 is opened, the dynamic stiffness reaches the maximum value at about 15Hz, the lag angle reaches the maximum value at about 12Hz, and the lag angle is larger in the frequency range of 5-15Hz, so that the vibration near the rigid body mode of the power assembly suspension system can be attenuated. When the first inertia channel 19 and the second inertia channel 20 are both opened, the dynamic stiffness is close to the minimum value at the idle excitation frequency point of about 23.7Hz according to the corresponding dynamic stiffness and lag angle curves, the suspended lag angle is larger near the excitation frequency point, the vibration at idle speed can be attenuated quickly, and the peak frequency of the lag angle is larger than 20Hz, so that the requirement is met.
Specifically, in the embodiment of the present application, when the pressure in the upper chamber 12 is greater than the pressure in the lower chamber 13, the pressure difference between the upper chamber 12 and the lower chamber 13 is denoted as P On the upper part I.e. when the combined pressure forces applied by the upper chamber 12 and the lower chamber 13 to the first valve 3 and the second valve 27 are both P On the upper part (ii) a When the pressure of the lower chamber 13 is set to be higher than the pressure of the upper chamber 12, the pressure difference between the lower chamber 13 and the upper chamber 12 is denoted as P Lower part I.e. when the lower chamber 13 and the upper chamber 12 apply a total force P to the first valve 3 and the second valve 27 Lower part . It will be understood by those skilled in the art that references to the pressure in the upper chamber 12 and the pressure in the lower chamber 13 in the embodiments of the present application refer to the pressure applied by the fluid in the upper chamber 12 or the fluid in the lower chamber 13 to the first movable disk 22 or the second movable disk 32.
From the foregoing analysis, it can be seen that, in the case where the pressure in the upper chamber 12 is greater than the pressure in the lower chamber 13, the first valve 3 and the second valve 27 are opened and closed as the pressure difference between the upper chamber 12 and the lower chamber 13 changes, as follows:
P on the upper part When P2 > P1, the first valve 3 is in a lower open state and the second valve 27 is in a lower closed state, and at this time, the first inertia passage 19 is open and the second inertia passage 20 is closed.
P2＞P On the upper part In the case of P1 or more, the first valve 3 is in a lower open state, and the second valve 27 is in an intermediate open state, at which time both the first inertia passage 19 and the second inertia passage 20 are open.
P1＞P On the upper part In the case of (1), the first valve 3 is in an intermediate closed state and the second valve 27 is in an intermediate open state, and at this time, the first inertia passage 19 is closed and the second inertia passage 20 is opened.
In the case where the pressure in the lower chamber 13 is greater than the pressure in the upper chamber 12, the opening and closing of the first valve 3 and the second valve 27 as the pressure difference between the pressure in the lower chamber 13 and the pressure in the upper chamber 12 changes are as follows:
P lower part In case P2 '> P1', the first valve 3 is in an upper open state and the second valve 27 is in a lower closed state, at which time the first inertia track 19 is open,the second inertia track 20 is closed.
P2’＞P Lower part P1', the first valve 3 is in the upward opening state and the second valve 27 is in the intermediate opening state, and both the first inertia passage 19 and the second inertia passage 20 are open.
P1’＞P Lower part In the case of (1), the first valve 3 is in an intermediate closed state and the second valve 27 is in an intermediate open state, and at this time, the first inertia passage 19 is closed and the second inertia passage 20 is opened.
The law that the dynamic stiffness and the lag angle of the suspension change along with the opening quantity of the inertia channels is analyzed. Specifically, the vibration amplitude of the powertrain is large when the vehicle is in a low-frequency vibration state, i.e., when the vehicle is in a starting condition, a rapid acceleration condition or an impact condition such as passing through an uneven road surface, and the pressure of the liquid in the upper chamber 12 is greater than or equal to P2, i.e., P2 On the upper part P2 is more than P1, and the analysis shows that the first valve 3 is in a lower opening state, the second valve 27 is in a lower closing state, at the moment, the first inertia channel 19 is opened, and the second inertia channel 20 is closed; alternatively, the average pressure in the lower chamber 13 is greater than or equal to P2', i.e. P Lower part P2 '> P1', it can be seen from the above analysis that the first valve 3 is in the upper open state, the second valve 27 is in the lower closed state, the first inertia track 19 is open, and the second inertia track 20 is closed. According to the analysis, only the first inertial channel 19 is opened under the low-frequency large-amplitude vibration, and according to the simulation analysis, the suspension has high dynamic stiffness at about 15Hz and large lag angle at about 12Hz, so that the vibration can be effectively attenuated, the overlarge displacement can be inhibited, the engine can be prevented from breaking through the limit, and the support is guaranteed to be effective.
Under the condition that the automobile power assembly is in an idling working condition, the vibration amplitude is smaller, the pressure of the upper chamber 12 is larger than or equal to P1 but smaller than P2, namely P2 is larger than P2 On the upper part P1 or more, and the analysis shows that the first valve 3 is in a lower opening state, the second valve 27 is in an intermediate opening state, and at the moment, the first inertia passage 19 and the second inertia passage 20 are both opened; alternatively, the pressure in the lower chamber 13 is greater than or equal to P1 'but less than P2', i.e.P2’＞P Lower part P1', the first valve 3 is in the upper open state and the second valve 27 is in the intermediate open state, and both the first inertia passage 19 and the second inertia passage 20 are open. That is, under the condition that the automobile power assembly is in the idle working condition, the first inertia channel 19 and the second inertia channel 20 are both opened, and according to the simulation analysis, the dynamic stiffness is close to the minimum value at the idle excitation frequency point of about 23.7Hz, and the suspension lag angle is larger near the excitation frequency point, so that the idle vibration of the engine can be effectively inhibited, and the comfort of the automobile is improved.
At low frequency large vibrations, the decoupling membrane 18 moves to its extreme position, the liquid mainly passing from said first inertia track 19 to the lower liquid chamber.
Under high-frequency vibration, namely when the automobile power assembly is in a high-speed cruising working condition, the vibration amplitude is smaller, the pressure of the upper chamber 12 is smaller than P1, namely P1 is larger than P On the upper part As can be seen from the above analysis, the first valve 3 is in the intermediate closed state, and the second valve 27 is in the intermediate open state, at which time the first inertia passage 19 is closed and the second inertia passage 20 is open; or the pressure in the lower chamber 13 is less than P1', i.e. P1' > P Lower part As can be seen from the above analysis, when the first valve 3 is in the intermediate closed state and the second valve 27 is in the intermediate open state, the first inertia passage 19 is closed and the second inertia passage 20 is open. From the above analysis, when the vehicle powertrain is in the high-speed cruising working condition, only the second valve 27 is in the intermediate opening state, the first valve 3 is in the intermediate closing state, that is, only the second inertia channel 20 is opened at this time, and the high-frequency dynamic hardening phenomenon occurs in the inertia channel at this time, and the decoupling film 18 vibrates up and down in the free stroke thereof, which is beneficial to reducing the hydraulic suspension high-frequency dynamic hardening phenomenon.
Although some specific embodiments of the present application have been described in detail by way of example, it should be understood by those skilled in the art that the above examples are for illustrative purposes only and are not intended to limit the scope of the present application. It will be appreciated by those skilled in the art that modifications may be made to the above embodiments without departing from the scope and spirit of the present application. The scope of the application is defined by the appended claims.
Claims (9)
1. A switchable multi-inertia channel powertrain hydraulic mount, comprising:
the liquid container comprises a shell, wherein a cavity is formed in the shell and is used for containing liquid;
the vibration isolation mechanism is arranged in the cavity and divides the cavity into an upper cavity and a lower cavity; a first inertia channel and a second inertia channel are arranged on the vibration isolation mechanism; the first inertia channel and the second inertia channel are both used for communicating the upper chamber and the lower chamber;
a first valve installed at an inlet of the first inertia passage and a second valve installed at an inlet of the second inertia passage;
the first valve and the second valve can be opened or closed according to the pressure difference between the upper chamber and the lower chamber, so that the upper chamber and the lower chamber are communicated through the first inertia passage and/or the second inertia passage;
the first valve comprises a first shell, a first moving disc, a first guide rod, a first inner spring and a first outer spring which are coaxially arranged, the first shell is provided with a first containing chamber, the first containing chamber comprises a first closed cavity and a first avoiding cavity which are sequentially distributed from top to bottom, and the inner diameter of the first avoiding cavity is larger than that of the first closed cavity; the outer diameter of the first moving disc is the same as the inner diameter of the first closed cavity;
the first guide rod is partially positioned in the first accommodating chamber and partially positioned outside the first accommodating chamber, a first upper limiting block is arranged on the part of the first guide rod positioned outside the first accommodating chamber, a lower limiting block is arranged on the part of the first guide rod positioned inside the first accommodating chamber, and the lower edge of the lower limiting block is aligned with the lower edge of the first avoidance cavity;
the first movable disc is sleeved on the part of the first guide rod between the first upper limiting block and the lower limiting block and can move between the first upper limiting block and the lower limiting block along the first guide rod;
the first inner spring is sleeved on the first guide rod, one end of the first inner spring is fixedly connected with the bottom of the first movable disc, the other end of the first inner spring is abutted to the bottom wall of the first containing chamber, the first outer spring is sleeved on the first guide rod, the bottom end of the first outer spring is abutted to the bottom wall of the first containing chamber, and the distance between the top end of the first outer spring and the lower surface of the first upper limiting block is larger than the thickness of the first movable disc under the condition that an engine is not started.
2. The switchable multi-inertia-channel power assembly hydraulic mount of claim 1, wherein the second valve comprises a second housing, a second movable plate, a second guide rod, a second inner spring and a second outer spring, the second inner spring and the second outer spring are coaxially arranged, the second housing is provided with a second accommodating chamber, the second accommodating chamber comprises a second upper closed chamber, a second avoiding chamber and a second lower closed chamber which are sequentially distributed from top to bottom, the inner diameter of the second avoiding chamber is larger than the inner diameters of the second upper closed chamber and the second lower closed chamber, and the outer diameter of the second movable plate is equal to the inner diameters of the second upper closed chamber and the second lower closed chamber;
the second guide rod is positioned in the second accommodating chamber, one end of the second guide rod is connected with a second upper limiting block, and the lower edge of the second upper limiting block is aligned with the opening of the second accommodating chamber;
the second movable disc is sleeved on the second guide rod and can move up and down along the second guide rod;
the second inner spring is sleeved on the second guide rod, one end of the second inner spring is fixedly connected with the bottom of the second movable plate, the other end of the second inner spring is abutted to the bottom wall of the second containing chamber, the second outer spring is sleeved on the second guide rod, the bottom end of the second outer spring is abutted to the bottom wall of the second containing chamber, and the distance between the top end of the second outer spring and the lower surface of the second upper limiting block is larger than the thickness of the second movable plate when an engine is not started.
3. The multi-inertia track type power assembly hydraulic mount capable of switching the states of claim 1, wherein the vibration isolation mechanism comprises an upper track plate, a lower track plate and a decoupling film, the upper track plate and the lower track plate are attached to each other and fixedly embedded in the inner wall of the cavity to separate the cavity into an upper cavity type and a lower cavity type, through holes are formed in the middle portions of the upper track plate and the lower track plate, part of the decoupling film is fixedly embedded in the through holes formed in the upper track plate, the other part of the decoupling film is embedded in the through holes formed in the lower track plate, the upper track plate forms the bottom wall of the upper cavity, and the lower track plate forms the top wall of the lower cavity;
the upper flow field plate and the lower flow field plate cooperate to form the first inertial channel and the second inertial channel.
4. The switchable multi-inertia track type power assembly hydraulic mount of claim 3, wherein the lower runner plate is provided with two C-shaped grooves on one side close to the upper runner plate, and the C-shaped openings of the two grooves are opposite;
the upper runner plate is provided with two openings, one of the openings is communicated with one end of the groove to form the first inertia channel; wherein another of said openings communicates with another of said recesses to form said second inertia track.
5. The switchable multi-inertia track powertrain hydraulic suspension of any one of claims 1 to 4, wherein a flexible membrane is disposed in the lower chamber, and the flexible membrane divides the lower chamber into a liquid chamber and an air chamber which are distributed up and down.
6. The switchable multi-inertia track powertrain hydraulic mount of claim 5, wherein the housing is provided with a vent in communication with the air chamber.
7. The switchable multi-inertia track powertrain hydraulic mount of claim 5, wherein the flexible membrane is a rubber membrane.
8. The switchable multi-inertia track powertrain hydraulic mount of any of claims 1-4, wherein the housing comprises an upper housing and a lower housing, the upper housing being removably coupled to the lower housing to form the housing.
9. The switchable multi-inertia track powertrain hydraulic mount of claim 8, wherein the upper housing has a main rubber spring and a reinforcing mass.
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| CN202111426749.9A CN113983114B (en) | 2021-11-27 | 2021-11-27 | Multi-inertia channel type power assembly hydraulic suspension with switchable states |
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| CN202111426749.9A CN113983114B (en) | 2021-11-27 | 2021-11-27 | Multi-inertia channel type power assembly hydraulic suspension with switchable states |
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| CN114593173B (en) * | 2022-03-04 | 2024-05-31 | 吉林大学 | Volume self-adjusting multi-inertia-channel hydraulic suspension based on magnetorheological liquid |
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| US4877225A (en) * | 1987-06-29 | 1989-10-31 | Bridgestone Corp. | Vibration isolator |
| JPH0771515A (en) * | 1993-09-06 | 1995-03-17 | Nippondenso Co Ltd | Electronic control engine mount |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| CN104100673A (en) * | 2014-07-22 | 2014-10-15 | 建新赵氏集团有限公司 | Semi-active control hydraulic suspension for automobile powertrain |
| CN106704470A (en) * | 2017-01-09 | 2017-05-24 | 重庆市锋盈汽车配件有限公司 | Self-adjusting automobile hydraulic mount |
| CN108488306A (en) * | 2018-03-28 | 2018-09-04 | 合肥工业大学 | A kind of self-adapting type multiple inertia tracks formula hydraulic mount and its adaptive approach |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017112168B4 (en) * | 2017-06-01 | 2021-04-29 | Vibracoustic Gmbh | Separating device for separating a working chamber and a compensation chamber of a hydraulically damping bearing as well as a hydraulically damping bearing |
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2021
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4877225A (en) * | 1987-06-29 | 1989-10-31 | Bridgestone Corp. | Vibration isolator |
| JPH0771515A (en) * | 1993-09-06 | 1995-03-17 | Nippondenso Co Ltd | Electronic control engine mount |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| CN104100673A (en) * | 2014-07-22 | 2014-10-15 | 建新赵氏集团有限公司 | Semi-active control hydraulic suspension for automobile powertrain |
| CN106704470A (en) * | 2017-01-09 | 2017-05-24 | 重庆市锋盈汽车配件有限公司 | Self-adjusting automobile hydraulic mount |
| CN108488306A (en) * | 2018-03-28 | 2018-09-04 | 合肥工业大学 | A kind of self-adapting type multiple inertia tracks formula hydraulic mount and its adaptive approach |
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