WO2021043281A1 - 液体复合弹簧及其刚度和阻尼调节方法 - Google Patents

液体复合弹簧及其刚度和阻尼调节方法 Download PDF

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Publication number
WO2021043281A1
WO2021043281A1 PCT/CN2020/113579 CN2020113579W WO2021043281A1 WO 2021043281 A1 WO2021043281 A1 WO 2021043281A1 CN 2020113579 W CN2020113579 W CN 2020113579W WO 2021043281 A1 WO2021043281 A1 WO 2021043281A1
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WIPO (PCT)
Prior art keywords
mandrel
damping
liquid chamber
liquid
channel
Prior art date
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PCT/CN2020/113579
Other languages
English (en)
French (fr)
Inventor
丁行武
卜继玲
李艺盟
刘桂杰
王凤
夏彰阳
Original Assignee
株洲时代新材料科技股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Priority claimed from CN201910840156.3A external-priority patent/CN110594342A/zh
Priority claimed from CN201910840263.6A external-priority patent/CN110735881A/zh
Application filed by 株洲时代新材料科技股份有限公司 filed Critical 株洲时代新材料科技股份有限公司
Priority to US17/423,434 priority Critical patent/US20220065326A1/en
Priority to EP20860133.6A priority patent/EP4027037A4/en
Publication of WO2021043281A1 publication Critical patent/WO2021043281A1/zh

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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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/16—Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads
    • 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
    • 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
    • F16F13/085—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 characterised by features of plastics springs; Attachment arrangements
    • 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
    • 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
    • F16F2226/00—Manufacturing; Treatments
    • F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/32—Modular design

Definitions

  • the invention relates to a hydraulic composite spring, in particular to a device for rail vehicles.
  • the invention also relates to a rigidity and damping adjustment method.
  • the present invention proposes a liquid composite spring, which has the function of damping vibration, and can provide variable stiffness and high damping effects; and a method for adjusting the stiffness and damping of the liquid composite spring, which can work according to different frequencies. Condition adjusts the stiffness of the liquid composite spring.
  • the present invention provides a liquid composite spring, including:
  • An upper liquid chamber provided in the upper part of the outer jacket, the lower end of the upper liquid chamber is connected to the top of the mandrel;
  • a lower liquid chamber arranged in the lower part of the outer jacket, the lower liquid chamber being connected to the mandrel;
  • the damping channel communicates with the liquid in the upper liquid chamber and the liquid in the lower liquid chamber.
  • the mandrel is prefabricated in multiple models, and a corresponding model is selected according to actual needs when installing the mandrel,
  • the damping passages in different types of mandrels have different lengths, cross-sectional areas, and different aspect ratios.
  • the damping flow passage is spirally arranged in the mandrel; the upper opening of the damping flow passage is axially arranged at the top end of the mandrel, and is connected to the upper end of the mandrel.
  • the liquid chamber is communicated; the lower end opening of the damping flow channel is arranged at the lower part of the mandrel in the radial direction, and is communicated with the lower liquid chamber.
  • the mandrel includes a mandrel inner core and a mandrel shell sleeved outside the inner core; wherein the outer wall of the mandrel inner core is provided with a spiral
  • the channel forms the main body of the damping flow channel; the mandrel shell is provided with a through hole along the radial direction, and the through hole communicates with the channel and the lower liquid chamber to form the damping flow channel
  • the lower end is open.
  • a certain space is provided between the upper liquid chamber and the lower liquid chamber, and a certain space is provided in the space to connect the upper liquid chamber and the lower liquid chamber.
  • the metal rubber main spring of the chamber is provided.
  • the metal rubber main spring includes a rubber body connected between the mandrel and the outer jacket, and a plurality of ring-shaped partitions arranged in a sleeve; the rubber body is filled in the partition Between the boards.
  • the jacket includes a cylindrical rigid jacket body, and a flexible sealing member that seals the lower end of the lower liquid chamber;
  • the outer edge of the sealing member is connected to the bottom of the jacket body, and the middle part is connected to the mandrel.
  • a metal ring is provided on the outer edge of the sealing member, and a convex structure that is clamped inside the mandrel is provided on the inner side of the sealing member;
  • the inner side of the bottom of the jacket main body is provided with a groove that cooperates with the metal ring; the metal ring is arranged in the groove and is connected to the outer wall by bolts.
  • a method for adjusting the stiffness of the above-mentioned liquid composite spring which includes:
  • Step one preparing a universal jacket for the liquid composite spring, and several different types of mandrels, and different damping channels are set in the different types of mandrels;
  • Step 2 According to the requirements of the actual frequency conditions, select the corresponding type of mandrel to adapt to the corresponding rigidity and damping; assemble the selected mandrel in the outer jacket, and install the metal rubber main spring in the outer jacket.
  • the upper part of the rubber main spring separates the upper liquid chamber, and the lower part separates the lower liquid chamber; wherein the damping channel of the mandrel connects the upper liquid chamber and the lower liquid chamber;
  • Step 3 The upper liquid chamber and the lower liquid chamber are filled with liquid, and the lower end of the jacket is sealed by a seal.
  • the multi-layer rubber body when the metal rubber main spring is installed, the multi-layer rubber body is vulcanized sequentially from the core shaft from the inside to the outside, and a ring-shaped partition is arranged between each layer of the rubber body, and the outermost layer The rubber body is connected to the inner wall of the jacket.
  • the length-to-diameter ratio between the damping channels in all the prepared mandrels is set within the range of 12-110 with a tolerance of 5.
  • the corresponding type of mandrel is selected; in the low frequency operating conditions, the mandrel of the damping channel with the aspect ratio greater than 26 is selected, and in the high frequency operating conditions Choose the mandrel of the damping runner with the aspect ratio less than 26.
  • the liquid composite spring of the present invention has an upper liquid chamber and a lower liquid chamber, and the upper liquid chamber and the lower liquid chamber are connected by a damping channel, and the liquid can pass through the inner core of the mandrel in the upper liquid chamber. Flow between the chamber and the lower liquid chamber. Thereby, the effect of vibration reduction is enhanced, and at the same time, it can provide variable stiffness and high damping performance.
  • the method for adjusting the stiffness and damping of the liquid composite spring of the present invention can adjust the stiffness and damping coefficient of the liquid composite spring according to actual frequency requirements, so that the liquid composite spring can meet the vibrations of various frequencies generated by the vehicle during driving. .
  • the method of the present invention meets different required stiffness and damping coefficients by preparing different types of mandrels. When adjusting the stiffness and damping, it can be completed only by replacing the mandrel, thereby realizing rapid replacement of the mandrel and liquid composite spring stiffness. adjust.
  • Figure 1 is a schematic structural diagram of a liquid composite spring according to an embodiment of the present invention.
  • Figure 2 is a schematic view of the three-dimensional structure of the inner core of the mandrel according to an embodiment of the present invention
  • Fig. 3 is a schematic cross-sectional structure diagram of an inner core of a mandrel according to an embodiment of the present invention.
  • Fig. 1 schematically shows a liquid composite spring according to an embodiment of the present invention.
  • the liquid can reciprocate in the upper and lower liquid chambers through the damping channel when vibrating, thereby providing variable stiffness and damping effects.
  • FIG. 1 schematically shows a liquid composite spring according to an embodiment of the present invention, including a mandrel 1.
  • a jacket 2 is connected to the upper part of the mandrel 1, and the lower part of the jacket 2 is sleeved on the upper part of the mandrel 1.
  • the upper part of the mandrel 1 is located inside the outer shell 2, and the lower part of the mandrel 1 is located outside the outer shell 2.
  • the upper space inside the jacket 2 is provided with an upper liquid chamber 3, and the middle of the lower part of the upper liquid chamber 3 is connected to the top end of the mandrel 1.
  • a lower liquid chamber 4 is provided at the lower part of the inside of the outer jacket 2, and a certain space is provided between the lower liquid chamber 4 and the upper liquid chamber 3.
  • a damping channel 11 is provided in the mandrel 1, and the damping channel 11 communicates the liquid in the upper liquid chamber 3 and the liquid in the lower liquid chamber 4.
  • the liquid composite spring is arranged on the bogie.
  • the mandrel 1 moves in the outer casing 2 and passes through the upper liquid chamber 3 and the lower liquid chamber in the liquid composite spring described in this embodiment.
  • the chamber 4 can flow liquid, thereby changing the space in the upper liquid chamber 3 and the lower liquid chamber 4 when the mandrel 1 moves. In the process of liquid circulation, the damping effect and stiffness of the liquid composite spring are changed.
  • the mandrel 1 is prefabricated in multiple models, and a corresponding model is selected according to actual needs when installing the mandrel 1, and the mandrel 1 can be replaced according to actual needs.
  • the damping channel 11 in the mandrel 1 of different models has different lengths and widths. If the cross section of the damping channel 11 is circular, the width is the length of the inner diameter. If the cross section of the damping channel 11 is rectangular, the width is The side length of the rectangle.
  • the type of the mandrel 1 is distinguished by the ratio of the length to the width of the damping flow passage 11 (length-to-diameter ratio).
  • the length of the damping channel 11 is selected.
  • the upper end opening of the damping channel 11 is axially arranged at the top end of the mandrel 1 and communicates with the upper liquid chamber 3. Wherein, the upper end of the mandrel 1 extends into the upper liquid chamber 3, and the bottom of the upper liquid chamber 3 is connected to the upper part of the mandrel 1 in the circumferential direction.
  • the lower end opening of the damping channel 11 is arranged at the lower part of the mandrel 1 along the radial direction of the mandrel 1 and communicates with the lower liquid chamber 4.
  • the number of the damping flow channel 11 may be multiple or one; the shape of the damping flow channel 11 may be a spiral or a strip structure.
  • the damping channel 11 can flow liquid between the upper liquid chamber 3 and the lower liquid chamber 4, and generate a certain amount of damping during the flow. force.
  • the damping channel 11 can generate a certain resistance during the flow of the liquid, make the liquid have a certain viscosity when flowing, and enhance the damping effect.
  • the damping flow channel 11 is spirally arranged in the mandrel 1.
  • the damping flow passage 11 is provided through the spiral structure, which increases the length of the damping flow passage 11 along the way, thereby enhancing the damping effect.
  • the mandrel 1 includes two parts, the mandrel inner core 12 and the mandrel shell 13 respectively.
  • the mandrel inner core 12 has a cylindrical structure, and the mandrel shell 13 is preferably a conical structure, and a hollow center that matches the shape of the mandrel inner core 12 is provided in the middle.
  • the mandrel shell 13 is sleeved outside the inner core 12 of the mandrel.
  • a spiral channel is provided on the outer wall of the inner core 12 of the mandrel to form the main body of the damping flow channel 11.
  • the mandrel shell 13 is provided with a through hole along the radial direction, and the through hole communicates with the channel and the lower liquid chamber 4 to form a lower end opening of the damping channel 11.
  • the mandrel 1 is provided with a mandrel inner core 12 and a mandrel shell 13, which facilitates the processing of the spiral damping flow passage 11 by combining the two parts.
  • the damping channel 11 is processed on the outer wall of the inner core 12 of the mandrel, and then assembled into the mandrel shell 13, which is convenient for processing.
  • a certain space is provided between the upper liquid chamber 3 and the lower liquid chamber 4, and the space is provided to connect the upper liquid chamber 3 and the lower liquid chamber.
  • the metal rubber main spring 23 is composed of metal and rubber materials, has a certain elasticity, and also has a certain rigidity.
  • the metal rubber main spring includes a rubber body 31, the middle part of the rubber body is connected to the mandrel 1, the outer part of the rubber body is connected to the outer casing 2, and the upper end is connected to the upper liquid chamber 3, and the lower end is connected to the lower liquid. Chamber 4.
  • the metal rubber main spring 23 further includes a plurality of partitions, and the partitions are sleeved.
  • the rubber body 31 is filled between the partitions.
  • the partition has a cylindrical or conical structure.
  • the partitions are sleeved and arranged.
  • the cross-sectional widths of the partitions are different, and the partitions with a larger width are sleeved outside the partitions with a smaller width and separated by a certain distance, thereby forming a structure with a circular cross-section.
  • the length of the partition located inside is relatively long, and the length of the partition located outside is relatively short, and the upper ends of the partitions are connected to the rubber body, and the horizontal height of the partition is relatively close.
  • the upper part of the lower liquid chamber 4 is arranged in a stepped structure, and the inner position is lower. In this way, when the mandrel 1 moves up and down, the rubber body and the sealing member 22 are driven to deform, thereby causing the partition to move up and down. Through the annular sleeve connection of a number of tapered partitions, the mandrel 1 will not be severely deviated in the horizontal direction during the expansion and contraction process.
  • the jacket 2 includes a rigid jacket body 21 and a flexible sealing member 22.
  • the jacket body 21 has a cylindrical structure, and the sealing member 22 is provided at the lower end of the jacket body 21. Wherein, the sealing member 22 seals the lower end of the lower liquid chamber 4.
  • the lower liquid chamber 4 is made into a flexible chamber by a flexible seal 22.
  • the outer edge of the sealing member 22 is connected to the bottom of the jacket body 21, and the middle part is connected to the mandrel 1.
  • a flexible sealing member 22 is provided at the bottom of the outer jacket 2 so that the lower liquid chamber 4 becomes a flexible liquid chamber.
  • the lower liquid chamber 4 can change the volume through deformation to ensure the smooth flow of the liquid.
  • the outer edge of the sealing member 22 is provided with a metal ring 24, and the inner bottom of the jacket body 21 is provided with a groove 25 that matches with the metal ring 24.
  • the groove 25 is an annular groove, and the metal ring 24 can be placed in the groove 25.
  • the metal ring 24 and the sealing member 22 are connected to the jacket body 21 by bolts.
  • a rubber pad 26 is further provided between the metal ring 24 and the groove 25.
  • a metal ring 24 is provided on the outer edge of the sealing member 22. Since the sealing member 22 is made of a flexible material, the metal ring 24 can be more firmly connected to the jacket body 21.
  • the casing body 21 is provided with a groove 25 for limiting the position of the metal ring 24 so that the screw holes correspond to each other, thereby facilitating disassembly and assembly.
  • the rubber gasket 26 enhances the sealing performance, so as to enhance the sealing performance of the lower liquid chamber 4 as a whole.
  • a convex structure 27 is provided on the inner side of the sealing member 22, and the convex structure 27 is fixed inside the mandrel 1.
  • the mandrel 1 is provided with a stepped structure, and the stepped structure is provided with a groove that matches the protrusion structure 27, and the protrusion structure 27 is clamped in the groove.
  • a metal gasket is provided under the step structure, and the metal gasket is provided at the other end of the raised structure 27 to fix the raised structure 27.
  • the sealing member 22 can be clamped inside the mandrel 1 through the protrusion structure 27, so that the sealing member 22 is firmly connected to the mandrel 1, and the sealing performance is enhanced.
  • a method for adjusting the stiffness and damping of a liquid composite spring which includes the following steps:
  • Step 1 Prepare the outer jacket 2 of the liquid composite spring.
  • the outer jacket 2 is universal, and the outer jackets 2 of different liquid composite springs are the same.
  • several mandrels 1 of different types are prepared, and different types of damping flow passages 11 are set in the mandrels 1 of different types.
  • Step two select the corresponding type of mandrel 1. Assemble the selected mandrel 1 in the outer casing 2, and install a metal rubber main spring in the outer casing 2.
  • the upper liquid chamber 3 is separated from the metal rubber main spring, and the lower liquid chamber 4 is separated from the lower; Wherein, the damping channel 11 of the mandrel 1 communicates with the upper liquid chamber 3 and the lower liquid chamber 4.
  • the step of selecting the mandrel 1 of the corresponding model can be to replace the entire mandrel 1, or to replace the different parts of the mandrel 1 (the inner core of the mandrel).
  • the mandrel 1 includes a mandrel inner core with different damping channels 11 and a mandrel shell 13 of the same structure, in the step of replacing the mandrel 1, the replacement of the mandrel inner core 12 can be realized by replacing the different mandrel inner core 12 The purpose of the axis 1 model.
  • Step three the upper liquid chamber 3 and the lower liquid chamber 4 are filled with liquid, and the lower end of the jacket 2 is sealed by a sealing member 22.
  • the sealing element 22 is a flexible sealing element 22.
  • the upper liquid chamber 3 and the lower liquid chamber 4 are connected through the damping channel 11, and the liquid can pass through the damping channel 11 in the upper liquid chamber 3 and the lower liquid chamber. Flow between 4, thereby enhancing the effect of damping.
  • the model of the mandrel 1 By changing the model of the mandrel 1, the overall stiffness and damping coefficient of the liquid composite spring can be changed.
  • different types of mandrels 1 are prepared to meet different rigidity or damping requirements. When adjusting the rigidity or damping, only the mandrel 1 needs to be replaced, thereby realizing rapid replacement of the mandrel 1 and liquid composite spring stiffness. adjust.
  • the multi-layer rubber body when the metal rubber main spring is installed, the multi-layer rubber body is vulcanized from the inside to the outside from the mandrel 1, an annular partition is arranged between each layer of the rubber body, and the outermost rubber body is connected to the The inner wall of the jacket 2 is described. In this way, the rubber body and the separator are vulcanized as a whole.
  • the length of the partition located inside is longer, the length of the partition located outside is shorter, the upper ends of the partitions are connected to the upper liquid chamber 3, and the level of the partition is relatively close.
  • the upper part of the lower liquid chamber 4 is arranged in a stepped structure, and the inner position is lower. In this way, when the mandrel 1 moves up and down, the rubber body and the sealing member 22 are driven to deform, thereby causing the partition to move up and down.
  • step 1 several mandrels 1 of different types are prepared, and different types of mandrels 1 are provided with different types of damping channels 11 to meet different rigidity and damping requirements.
  • Different types of damping channels 11 have different sizes, such as different widths and lengths, or have different shapes and structures.
  • the cross section of the damping channel 11 is preferably a rectangular structure, and may also be trapezoidal, arc-shaped and other structures capable of connecting the upper liquid chamber 3 and the lower liquid chamber 4.
  • the length-diameter ratios of different types of damping flow passages 11 are different.
  • the tolerance between the length-diameter ratios of the different types of damping flow passages 11 is 5, and the length-diameter ratio is set in the range of 12-110.
  • the number of models of the mandrel 1 is 20, the tolerance between the length-diameter ratio of the damping channel 11 is 5, and the smallest length-diameter ratio is 15. Then, the length-to-diameter ratio of the damping channel 11 in the prepared mandrel 1 is 15, 20, 25, 30...100, 105, 110, respectively.
  • damping channels 11 have different aspect ratios.
  • the damping flow channel 11 with a relatively large length and diameter is used for a liquid composite spring with relatively large rigidity and damping required, and is suitable for a situation with a small vibration frequency.
  • the flow damping channel 11 with a relatively small length and diameter is used for a liquid composite spring with a small required rigidity and damping, and is suitable for a situation with a large vibration frequency.
  • step 1 the corresponding type and number of mandrels 1 are selected according to the requirements of the actual frequency operating conditions. Under low frequency conditions, such as the vibration frequency is less than 15Hz, choose the mandrel 1 with the length to diameter ratio of the damping channel 11 greater than 26; under high frequency conditions, if the vibration frequency is greater than 15Hz, choose the length of the damping channel 11 Mandrel 1 with diameter ratio less than 26.
  • the damping flow channel 11 is spirally arranged in the mandrel 1.
  • the damping flow passage 11 is provided through the spiral structure, which increases the length of the damping flow passage 11 along the way, thereby enhancing the damping effect.
  • the upper end opening of the damping channel 11 is axially arranged at the top end of the mandrel 1 and communicates with the upper liquid chamber 3; the lower end opening of the damping channel 11 is radially arranged on the mandrel 1 and communicate with the lower liquid chamber 4.
  • the upper and lower parts of the mandrel housing 13 are respectively provided with through holes along the radial direction, and the through holes in the upper part of the mandrel housing 13 communicate with the channel and the upper liquid chamber.
  • the chamber 3 forms the upper end opening of the damping flow passage 11; the through hole at the lower part of the mandrel shell 13 communicates the channel and the lower liquid chamber 4 to form the lower end opening of the damping flow passage 11.
  • the cross-sectional area of the spiral flow channel, the pitch, and the number of flow channels can be adjusted to achieve changes in dynamic performance (dynamic stiffness, damping).
  • the size and number of runners can be calculated to achieve rapid replacement of runners.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

一种液体复合弹簧及其刚度和阻尼调节方法，该液体复合弹簧用于车辆、尤其是轨道车辆，包括芯轴(1)；外套(2)，其套设在芯轴(1)的上部，芯轴(1)的上部位于外套(2)的内部，芯轴(1)的下部位于外套(2)的外部；设置在外套(2)内的上部的上液体腔室(3)，上液体腔室(3)的下端连接芯轴(1)的顶部；以及设置在外套(2)内的下部的下液体腔室(4)，下液体腔室(4)与芯轴(1)相连；其中，芯轴(1)内设置有阻尼流道(11)，阻尼流道(11)连通上液体腔室(3)内的液体和下液体腔室(4)内的液体。该液体复合弹簧具有减振的功能，同时能够改变刚度和阻尼效果。

Description

液体复合弹簧及其刚度和阻尼调节方法 技术领域
本发明涉及一种液压复合弹簧，尤其涉及一种用于轨道车辆的装置。本发明还涉及一种刚度和阻尼调节方法。
背景技术
车辆在轨道上行驶时，伴随产生复杂的振动现象，因此铁路车辆上安装衰减机械振动的弹簧阻尼装置是必不可少的。传统的橡胶锥形弹簧容易获得垂向、横向和纵向不同的静态刚度值，具有明显的弹性变形特征，能够满足一般轴箱悬挂要求。但是由于橡胶材料的局限性，橡胶锥形弹簧随着频率的增加动刚度先缓慢增加后趋于平稳，非线性频变特性不明显；同时，橡胶材料的阻尼较小，对振动能量的耗散能力有限。
发明内容
针对上述问题，本发明提出了一种液体复合弹簧，具有减振的功能，同时能够提供变刚度和高阻尼效果；以及一种液体复合弹簧的刚度和阻尼的调节方法，能够根据不同的频率工况调节液体复合弹簧的刚度。
本发明提出了一种液体复合弹簧，包括：
外套；
连接所述外套的芯轴，所述芯轴内设置有阻尼流道，所述芯轴的上部位于所述外套的内部，所述芯轴的下部位于所述外套的外部；
设置在所述外套内的上部的上液体腔室，所述上液体腔室的下端连接所述芯轴的顶部；以及
设置在所述外套内的下部的下液体腔室，所述下液体腔室与所述芯轴相连；
其中，所述阻尼流道连通上液体腔室内的液体和所述下液体腔室内的液体。
进一步地，在一个优选的实施方式中，所述芯轴预制多种型号，安装所述芯轴时根据实际需要选取相应的一个型号，
其中，不同型号的芯轴内的阻尼流道具有不同的长度、横截面积以及长径比不同。
进一步地，在一个优选的实施方式中，所述阻尼流道呈螺旋型设置在所述芯轴内；所述阻尼流道的上端开口沿轴向设置在芯轴的顶端，并与所述上液体腔室相连通；所述阻尼流道的下端开口沿径向设置在所述芯轴的下部，并与所述下液体腔室相连通。
进一步地，在一个优选的实施方式中，所述芯轴包括芯轴内芯和套接在所述内芯外的芯轴外壳；其中，所述芯轴内芯的外壁上设置有螺旋型的槽道，形成所述阻尼流道的主体；所述芯轴外壳上设置有沿径向的通孔，所述通孔连通所述槽道和所述下液体腔室，形成所述阻尼流道的下端开口。
进一步地，在一个优选的实施方式中，所述上液体腔室和所述下液体腔室之间设置有一定的空间，所述空间内设置有连接所述上液体腔室和所述下液体腔室的金属橡胶主簧。
进一步地，在一个优选的实施方式中，所述金属橡胶主簧包括连接在芯轴和外套之间的橡胶体，以及若干套接设置的环形的隔板；所述橡胶体填充在所述隔板之间。
进一步地，在一个优选的实施方式中，所述外套包括筒形的刚性的外套主体，以及柔性的密封件，所述密封件密封所述下液体腔室的下端；
其中，所述密封件的外部边缘连接所述外套主体的底部，其中部连接所述芯轴。
进一步地，在一个优选的实施方式中，所述密封件的外侧边缘设置有金属环，所述密封件的内侧设置有卡接在所述芯轴内部的凸起结构；
并且，所述外套主体的底部内侧设置有与所述金属环配合的凹槽；所述金属环设置在所述凹槽内，并通过螺栓连接所述外壁。
根据本发明的另一个方面还提出了一种上述液体复合弹簧的刚度调节方法，其包括：
步骤一，制备液体复合弹簧的通用的外套，以及若干不同型号的芯轴，不同型号的所述芯轴内设置不同的阻尼流道；
步骤二，根据实际频率工况的要求，选取相应型号芯轴，以适应相应的刚度和阻尼；将选取的芯轴组装在所述外套内，并在所述外套内安装金属橡胶主簧， 金属橡胶主簧的上方分隔出上液体腔室，下方分隔出下液体腔室；其中，芯轴的阻尼流道连通所述上液体腔室和所述下液体腔室；
步骤三，向上液体腔室和下液体腔室内充满液体，并在外套的下端通过密封件密封。
进一步地，在一个优选的实施方式中，安装金属橡胶主簧时，从芯轴开始由内向外依次硫化多层橡胶体，每层橡胶体之间设置环形的隔板，并将最外层的橡胶体连接所述外套的内壁上。
进一步地，在一个优选的实施方式中，所有制备的所述芯轴内的阻尼流道之间的长径比以5为公差设置在12～110范围内。
进一步地，在一个优选的实施方式中，根据实际频率工况的要求，选取相应型号的芯轴；在低频工况下选用长径比大于26的阻尼流道的芯轴，在高频工况下选用长径比小于26的阻尼流道的芯轴。
与现有技术相比，本发明的优点在于：
本发明所述的液体复合弹簧，具有上液体腔室和下液体腔室，并且上液体腔室和下液体腔室之间通过阻尼流道相连通，液体能够通过芯轴内芯在上液体腔室和下液体腔室之间流动。从而增强了减振的效果，同时能够提供变刚度和高阻尼性能。
本发明所述的液体复合弹簧的刚度和阻尼调节方法，能够根据实际的频率的需要调节液体复合弹簧的刚度和阻尼系数，使液体复合弹簧能够满足车辆在行驶过程中产生的各种频率的振动。本发明的方法，通过制备不同类型的芯轴来满足不同需要的刚度和阻尼系数，在调节刚度和阻尼时，只需要更换芯轴就能够完成，从而实现芯轴的快速置换和液体复合弹簧刚度调节。
附图说明
图1是根据本发明的一个实施方案的液体复合弹簧的结构示意图；
图2是根据本发明的一个实施方案的芯轴内芯的立体结构示意图；
图3是根据本发明的一个实施方案的芯轴内芯的剖面结构示意图。
在附图中，相同的部件使用相同的附图标记。附图并未按照实际的比例绘制。
在附图中各附图标记的含义如下：1、芯轴，2、外套，3、上液体腔室，4、下液体腔室，11、阻尼流道，12、芯轴内芯，13、芯轴外壳，21、外套主体，22、 密封件，23、金属橡胶主簧，24、金属环，25、凹槽，26、橡胶垫，27、凸起结构，31、橡胶体。
具体实施方式
下面将结合附图对本发明作进一步说明。
图1示意性地显示了根据本发明的一个实施例的液体复合弹簧。根据本发明的液体复合弹簧，尤其能够在振动时，液体通过阻尼流道在上、下液体腔室内往复流动，从而提供了变刚度和阻尼效果。
图1示意性地显示了根据本发明的一个实施例的液体复合弹簧，包括芯轴1。所述芯轴1上部连接有外套2，所述外套2的下部套设在所述芯轴1的上部。其中，所述芯轴1的上部位于所述外套2的内部，所述芯轴1的下部位于所述外套2的外部。所述外套2的内部的上部空间设置有上液体腔室3，所述上液体腔室3的下部的中部连接所述芯轴1的顶端。所述外套2的内部的下部设置有下液体腔室4，所述下液体腔室4与所述上液体腔室3之间设置有一定的空间。在本实施例中，所述芯轴1内设置有阻尼流道11，所述阻尼流道11连通上液体腔室3内的液体和所述下液体腔室4内的液体。
在根据本实施例所述的液体复合弹簧中，所述液体复合弹簧设置在转向架上。当车辆在轨道上行驶过程中产生振动时，所述芯轴1在所述外套2内移动，通过本实施例所述的液体复合弹簧中的所述上液体腔室3和所述下液体腔室4能够流动液体，从而在芯轴1移动时改变上液体腔室3和下液体腔室4内的空间。在液体流通的过程中改变液体复合弹簧的阻尼效果和刚度。
在一个实施例中，所述芯轴1预制多种型号，安装所述芯轴1时根据实际需要选取相应的一个型号，并且根据实际需要可以置换芯轴1。不同型号的芯轴1内的阻尼流道11具有不同的长度和宽度，如果阻尼流道11的截面为圆形，则宽度为内径的长度，如果阻尼流道11的截面为矩形，则宽度为矩形的边长。在本实施例中，芯轴1的类型以阻尼流道11的长度和宽度的比(长径比)来区分。
在使用本实施例所述的液体复合弹簧时，根据实际频率工况的要求，选取相应型号的芯轴1时，在低频工况下，如振动频率小于15Hz时，选用阻尼流道11的长径比大于26的芯轴1；在高频工况下，如振动频率大于15Hz时，选用阻尼流道11的长径比小于26的芯轴1。
在一个实施例中，所述阻尼流道11的上端开口沿轴向设置在芯轴1的顶端，并与所述上液体腔室3相连通。其中，芯轴1的上端伸入到上液体腔室3的内部，上液体腔室3的底部连接在芯轴1的上部的周向上。所述阻尼流道11的下端开口沿芯轴1的径向设置在所述芯轴1的下部，并与所述下液体腔室4相连通。在本实施例中，阻尼流道11的数量可以是多个，也可以是一个；阻尼流道11的形状可以是螺旋型的也可以是条形的结构。
在根据本实施例所述的液体复合弹簧中，通过阻尼流道11能够在所述上液体腔室3和所述下液体腔室4之间的流通液体，并在流动过程中产生一定的阻尼力。阻尼流道11能够使液体流动过程中产生一定的阻力，使液体在流动时具有一定的粘滞性，增强阻尼效果。
在一个实施例中，所述阻尼流道11呈螺旋型设置在所述芯轴1内。通过螺旋型结构设置阻尼流道11，增加了阻尼流道11的沿程长度，从而增强了阻尼效果。
在一个优选的实施例中，所述芯轴1包括两部分，分别为芯轴内芯12和芯轴外壳13。芯轴内芯12为圆柱形结构，芯轴外壳13优选为圆锥形的结构，中部设置与芯轴内芯12形状相匹配的空心。芯轴外壳13套在芯轴内芯12的外部。在本实施例中，所述芯轴内芯12的外壁上设置有螺旋型的槽道，形成所述阻尼流道11的主体。所述芯轴外壳13上设置有沿径向的通孔，所述通孔连通所述槽道和所述下液体腔室4，形成所述阻尼流道11的下端开口。
在根据本实施例所述的液体复合弹簧中，芯轴1设置芯轴内芯12和芯轴外壳13，通过两部分组合的方式，便于加工螺旋型阻尼流道11。在芯轴内芯12的外壁上加工阻尼流道11，再组装到芯轴外壳13内，这样便于加工。
在一个实施例中，所述上液体腔室3和所述下液体腔室4之间设置有一定的空间，所述空间内设置有连接所述上液体腔室3和所述下液体腔室4的金属橡胶主簧23，金属橡胶主簧23由金属和橡胶材质构成，具有一定的弹性，同时也具有一定的刚性。
在一个实施例中，所述金属橡胶主簧包括橡胶体31，所述橡胶体的中部连接芯轴1，外部连接所述外套2，其上端连接所述上液体腔室3，下端连接下液体腔室4。
在根据本实施例所述的液体复合弹簧中，所述金属橡胶主簧23还包括若干 隔板，所述隔板之间套接设置。其中，所述橡胶体31填充在隔板之间。在本实施例中，所述隔板为筒形或锥形结构。所述隔板之间套接设置。其中，所述隔板的截面宽度不同，宽度较大的隔板套在宽度较小的隔板外，并间隔一定的距离，从而形成截面为环形的结构。优选地，在本实施例中位于内部的隔板的长度较长，位于外部的隔板的长度较短，隔板的上端均连接所述橡胶体，其水平高度相对接近。下液体腔室4的上部设置为阶梯状的结构，靠内的位置较低。这样，在芯轴1上下移动时，带动橡胶体和密封件22发生形变，从而使所述隔板上下移动。通过若干锥形的隔板环形套接，使芯轴1在伸缩的过程中，在水平方向不会出现严重的偏差。
在一个实施例中，所述外套2包括刚性的外套主体21，以及柔性的密封件22。所述外套主体21为筒形结构，所述密封件22设置在外套主体21的下端。其中，所述密封件22密封所述下液体腔室4的下端。通过柔性的密封件22使所述下液体腔室4成为柔性的腔室。其中，所述密封件22的外部边缘连接所述外套主体21的底部，其中部连接所述芯轴1。
在使用根据本实施例所述的液体复合弹簧时，所述外套2的底部设置柔性的密封件22，使所述下液体腔室4成为柔性液体腔室。在液体流动的过程中，下液体腔室4能够通过形变来改变体积，保证液体顺利流动。在芯轴1移动时，芯轴1与外套2的相对位置发生变化，从而带动液体流动，从而起到减振的效果。
在一个优选的实施例中，所述密封件22的外侧边缘设置有金属环24，所述外套主体21的底部内侧设置有与所述金属环24配合的凹槽25。所述凹槽25为环形的凹槽，金属环24能够放置在所述凹槽25内。其中，金属环24、密封件22通过螺栓连接所述外套主体21。优选地，所述金属环24与所述凹槽25之间还设置有橡胶垫26。
在根据本实施例所述的液体复合弹簧中，所述密封件22的外侧边缘设置有金属环24。由于所述密封件22采用柔性材质，通过金属环24能够更加稳固地与所述外套主体21相连。所述外套主体21上设置有凹槽25，用于限定金属环24的位置，使螺孔对应，从而便于拆装。通过所述橡胶垫26增强密封性，以增强下液体腔室4整体的密封性。
在一个实施例中，所述密封件22的内侧设置有凸起结构27，所述凸起结构27固定在所述芯轴1的内部。在本实施例中，所述芯轴1上设置有台阶结构，所 述台阶结构上设置有与所述凸起结构27相配合的卡槽，凸起结构27卡接在所述卡槽内。所述台阶结构的下方设置有金属垫片，所述金属垫片设置在凸起结构27的另一端，从而将凸起结构27固定。
在根据本实施例所述的液体复合弹簧中，密封件22通过凸起结构27能够卡接在芯轴1的内部，从而使密封件22与芯轴1稳固地连接，并且增强了密封性。
根据本发明的另一个方面，还提出了一种液体复合弹簧的刚度和阻尼调节方法，其包括如下步骤：
步骤一，制备液体复合弹簧的外套2，外套2具有通用性，不同的液体复合弹簧的外套2是相同的。并且制备若干不同型号的芯轴1，不同型号的芯轴1内设置不同类型的阻尼流道11。
步骤二，根据实际频率工况的要求，选取相应型号的芯轴1。将选取的芯轴1组装在所述外套2内，并在所述外套2内安装金属橡胶主簧，金属橡胶主簧的上方分隔出上液体腔室3，下方分隔出下液体腔室4；其中，芯轴1的阻尼流道11连通所述上液体腔室3和所述下液体腔室4。在本实施例中，选取相应型号的芯轴1的步骤可以是更换整个芯轴1，也可以更换芯轴1中具有差异的部件(芯轴内芯)。由于芯轴1包括具有不同阻尼流道11的芯轴内芯，以及相同结构的芯轴外壳13，在更换芯轴1的步骤中，可以通过更换具有差异的芯轴内芯12来实现更换芯轴1型号的目的。
步骤三，向上液体腔室3和下液体腔室4内充满液体，并在外套2的下端通过密封件22密封。其中，密封件22为柔性的密封件22。结构受整体振动载荷时，在液体复合弹簧的上液体腔室3和下液体腔室4之间流通流体，并且在流体流动时产生一定的阻尼力。选取不同的阻尼流道11的芯轴1以适应相应的刚度和阻尼系数，这样，改变阻尼流道11的类型能够改变液体复合弹簧整体的刚度和阻尼系数。
在根据本实施例所述的方法中，上液体腔室3和下液体腔室4之间通过阻尼流道11相连通，液体能够通过阻尼流道11在上液体腔室3和下液体腔室4之间流动，从而增强了减振的效果。通过改变芯轴1的型号能够改变液体复合弹簧整体的刚度和阻尼系数。本实施例通过制备不同型号的芯轴1来满足不同需求的刚度或阻尼，在调节刚度或阻尼时，只需要更换芯轴1就能够完成，从而实现芯轴1的快速置换和液体复合弹簧刚度调节。
在一个实施例中，安装金属橡胶主簧时，从芯轴1开始由内向外依次硫化多层橡胶体，每层橡胶体之间设置环形的隔板，并将最外层的橡胶体连接所述外套2的内壁上。这样，橡胶体和隔板硫化成一个整体。
在根据本实施例所述的方法中，位于内部的隔板的长度较长，位于外部的隔板的长度较短，隔板的上端均连接所述上液体腔室3，其水平高度相对接近。下液体腔室4的上部设置为阶梯状的结构，靠内的位置较低。这样，在芯轴1上下移动时，带动橡胶体和密封件22发生形变，从而使所述隔板上下移动。
在一个实施例中，在步骤一中，制备若干不同型号的芯轴1，不同型号的芯轴1设置不同类型的阻尼流道11，以适应不同的刚度和阻尼要求。不同类型的阻尼流道11具有不同的尺寸，如不同的宽度、长度，或具有不同的形状、结构。阻尼流道11的横截面优选为矩形结构，也可以是梯形、弧形等其他能够连通上液体腔室3和下液体腔室4的结构。并且不同类型的阻尼流道11的长径比不同。
在一个优选的实施例中，不同类型阻尼流道11以所述长径比之间的公差为5，并且长径比设置在12～110的范围内。例如，芯轴1的型号的数量为20个，其阻尼流道11长径比之间的公差为5，长径比最小的为15。那么，制备的芯轴1中的阻尼流道11的长径比分别为15、20、25、30……100、105、110。
在根据本实施例所述的方法中，不同类型的阻尼流道11，具有不同长径比。长径比较大的阻尼流道11，用于要求的刚度和阻尼较大的液体复合弹簧，适合振动频率较小的情况。长径比较小的流阻尼流道11，用于要求的刚度和阻尼较小的液体复合弹簧，适合振动频率较大的情况。
在一个实施例中，在步骤一中，根据实际频率工况的要求，选取相应类型和数量的芯轴1。在低频工况下，如振动频率小于15Hz时，选用阻尼流道11的长径比大于26的芯轴1；在高频工况下，如振动频率大于15Hz时，选用阻尼流道11的长径比小于26的芯轴1。
在一个实施例中，如图2和图3所示，所述阻尼流道11呈螺旋型设置在所述芯轴1内。通过螺旋型结构设置阻尼流道11，增加了阻尼流道11的沿程长度，从而增强了阻尼效果。所述阻尼流道11的上端开口沿轴向设置在芯轴1的顶端，并与所述上液体腔室3相连通；所述阻尼流道11的下端开口沿径向设置在所述芯轴1的下部，并与所述下液体腔室4相连通。
在一个实施例中，所述芯轴外壳13的上部和下部分别设置有沿径向的通孔， 所述芯轴外壳13的上部的所述通孔连通所述槽道和所述上液体腔室3，形成所述阻尼流道11的上端开口；所述芯轴外壳13的下部的所述通孔连通所述槽道和所述下液体腔室4，形成阻尼流道11的下端开口。
在制作根据本实施例所述方法中的芯轴1时，可以进行螺旋流道的截面积大小、螺距以及流道数量的调整以实现动态性能(动刚度、阻尼)的变化。在不同的动态性能要求下，可以通过计算来得到流道的尺寸、条数等参数，以实现流道的快速置换。
虽然已经参考优选实施例对本发明进行了描述，但在不脱离本发明的范围的情况下，可以对其进行各种改进并且可以用等效物替换其中的部件。尤其是，只要不存在结构冲突，各个实施例中所提到的各项技术特征均可以任意方式组合起来。本发明并不局限于文中公开的特定实施例，而是包括落入权利要求的范围内的所有技术方案。

Claims (12)

  1. 一种液体复合弹簧，包括：
    外套；
    连接所述外套的芯轴，所述芯轴内设置有阻尼流道，所述芯轴的上部位于所述外套的内部，所述芯轴的下部位于所述外套的外部；
    设置在所述外套内的上部的上液体腔室，所述上液体腔室的下端连接所述芯轴的顶部；以及
    设置在所述外套内的下部的下液体腔室，所述下液体腔室与所述芯轴相连；
    其中，所述阻尼流道连通上液体腔室内的液体和所述下液体腔室内的液体。
  2. 根据权利要求1所述的液体复合弹簧，其特征在于，所述芯轴预制多种型号，安装所述芯轴时根据实际需要选取相应的一个型号，
    其中，不同型号的芯轴内的阻尼流道具有不同的长度、横截面积以及长径比不同。
  3. 根据权利要求2所述的液体复合弹簧，其特征在于，所述阻尼流道呈螺旋型设置在所述芯轴内；所述阻尼流道的上端开口沿轴向设置在芯轴的顶端，并与所述上液体腔室相连通；所述阻尼流道的下端开口沿径向设置在所述芯轴的下部，并与所述下液体腔室相连通。
  4. 根据权利要求3所述的液体复合弹簧，其特征在于，所述芯轴包括芯轴内芯和套接在所述内芯外的芯轴外壳；其中，所述芯轴内芯的外壁上设置有螺旋型的槽道，形成所述阻尼流道的主体；所述芯轴外壳上设置有沿径向的通孔，所述通孔连通所述槽道和所述下液体腔室，形成所述阻尼流道的下端开口。
  5. 根据权利要求1至4中任一项所述的液体复合弹簧，其特征在于，所述上液体腔室和所述下液体腔室之间设置有一定的空间，所述空间内设置有连接所述上液体腔室和所述下液体腔室的金属橡胶主簧。
  6. 根据权利要求5所述的液体复合弹簧，其特征在于，所述金属橡胶主簧包括连接在芯轴和外套之间的橡胶体，以及若干套接设置的环形的隔板；所述橡胶体填充在所述隔板之间。
  7. 根据权利要求6所述的液体复合弹簧，其特征在于，所述外套包括筒形的刚性的外套主体，以及柔性的密封件，所述密封件密封所述下液体腔室的下端；
    其中，所述密封件的外部边缘连接所述外套主体的底部，其中部连接所述芯轴。
  8. 根据权利要求7所述的液体复合弹簧，其特征在于，所述密封件的外侧边缘设置有金属环，所述密封件的内侧设置有卡接在所述芯轴内部的凸起结构；
    并且，所述外套主体的底部内侧设置有与所述金属环配合的凹槽；所述金属环设置在所述凹槽内，并通过螺栓连接所述外壁。
  9. 一种根据权利要求1至8所述的液体复合弹簧的刚度和阻尼调节方法，其特征在于，包括：
    步骤一，制备液体复合弹簧的通用的外套，以及若干不同型号的芯轴，不同型号的所述芯轴内设置不同的阻尼流道；
    步骤二，根据实际频率工况的要求，选取相应型号芯轴，以适应相应的刚度和阻尼；将选取的芯轴组装在所述外套内，并在所述外套内安装金属橡胶主簧，金属橡胶主簧的上方分隔出上液体腔室，下方分隔出下液体腔室；其中，芯轴的阻尼流道连通所述上液体腔室和所述下液体腔室；
    步骤三，向上液体腔室和下液体腔室内充满液体，并在外套的下端通过密封件密封。
  10. 根据权利要求9所述的刚度和阻尼调节方法，其特征在于，安装金属橡胶主簧时，从芯轴开始由内向外依次硫化多层橡胶体，每层橡胶体之间设置环形的隔板，并将最外层的橡胶体连接所述外套的内壁上。
  11. 根据权利要求10所述的刚度和阻尼调节方法，其特征在于，所有制备的所述芯轴内的阻尼流道之间的长径比以5为公差设置在12～110范围内。
  12. 根据权利要求11所述的刚度和阻尼调节方法，其特征在于，根据实际频率工况的要求，选取相应型号的芯轴；在低频工况下选用长径比大于26的阻尼流道的芯轴，在高频工况下选用长径比小于26的阻尼流道的芯轴。
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