CN212643402U - Power assembly hydraulic suspension and car - Google Patents
Power assembly hydraulic suspension and car Download PDFInfo
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- CN212643402U CN212643402U CN202021237828.6U CN202021237828U CN212643402U CN 212643402 U CN212643402 U CN 212643402U CN 202021237828 U CN202021237828 U CN 202021237828U CN 212643402 U CN212643402 U CN 212643402U
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Abstract
An object of the utility model is to provide a power assembly hydraulic pressure suspension and car makes hydraulic pressure suspension show big damping of big dynamic stiffness under big amplitude excitation and show little damping of dynamic stiffness and do not have the comprehensive properties of striking abnormal sound under little amplitude excitation. This power assembly hydraulic suspension includes: the decoupling membrane is arranged in the flow channel assembly; an inertia channel communicated with an upper liquid chamber positioned above the flow channel assembly and a lower liquid chamber positioned below the flow channel assembly is formed on the flow channel assembly; the decoupling film is provided with at least two pressure relief holes which are communicated with an upper liquid chamber positioned above the flow channel assembly and a lower liquid chamber positioned below the flow channel assembly; the ratio of the sum of the cross-sectional areas of the pressure relief holes to the cross-sectional area of the inertia channel is 1:14 to 1: 16.
Description
Technical Field
The utility model relates to an automobile parts field specifically is a power assembly hydraulic pressure suspension and car.
Background
At present, the installation mode of a hydraulic suspension decoupling membrane is axial fixation, and two modes are common. One is a floating decoupling film, namely the decoupling film is in clearance fit with the upper cover and the lower cover of the runner, as shown in fig. 1; under the excitation of small amplitude, the decoupling film can move up and down, and the characteristic of small rigidity and small damping is shown; under large-amplitude excitation, liquid in the upper chamber and the lower chamber mainly flows through the inertia channel, the characteristics of large rigidity and large damping are shown, and meanwhile, decoupling membrane impact sound is easily generated. The other is a fixed decoupling film, namely the decoupling film is pressed by the upper cover and the lower cover of the runner, as shown in fig. 2; under the excitation of small amplitude, liquid mainly flows through the inertia channel, and the large-rigidity large-damping characteristic is shown.
Through patent search, CN201611094664.4 "decoupling membrane and liquid resistance suspension including the same" and CN201520416955.5 "decoupling membrane for hydraulic suspension". The middle of the hydraulic suspension decoupling membranes introduced in the two patents is respectively provided with a three-fork type overflow hole and a circular overflow hole, and under the excitation of large amplitude such as a bumpy road, liquid in an upper chamber and a lower chamber of the hydraulic suspension can flow through the overflow holes, so that the up-and-down movement of the decoupling membranes is weakened, and the impact abnormal sound of the decoupling membranes and the upper flow channel cover plate and the lower flow channel cover plate can be relieved. The two overflow holes of the invention mainly solve the problem of abnormal impact sound of the decoupling diaphragm under large-amplitude excitation; however, both schemes still suffer from insufficient performance due to: due to the fact that the aperture of the overflow hole formed in the decoupling diaphragm is too large, under the excitation of large amplitude, most of liquid in the upper cavity and the lower cavity cannot flow through the inertia channel but flow through the overflow hole, and performance characteristics of low frequency, large damping and large dynamic stiffness cannot be presented.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a power assembly hydraulic pressure suspension and car makes hydraulic pressure suspension show big damping of big dynamic stiffness under big amplitude excitation and show little damping of dynamic stiffness and do not have the comprehensive properties of striking abnormal sound under little amplitude excitation.
The technical scheme of the utility model is that:
the utility model provides a power assembly hydraulic pressure suspension, include:
the decoupling membrane is arranged in the flow channel assembly;
an inertia channel communicated with an upper liquid chamber positioned above the flow channel assembly and a lower liquid chamber positioned below the flow channel assembly is formed on the flow channel assembly;
the decoupling film is provided with at least two pressure relief holes which are communicated with an upper liquid chamber positioned above the flow channel assembly and a lower liquid chamber positioned below the flow channel assembly;
the ratio of the sum of the cross-sectional areas of the pressure relief holes to the cross-sectional area of the inertia channel is 1:14 to 1: 16.
Preferably, the flow channel assembly comprises:
the upper runner cover and the lower runner cover are oppositely arranged and fixedly connected, and an annular groove for mounting the decoupling film is formed between the upper runner cover and the lower runner cover;
a first annular groove is formed in the end face, facing the upper liquid chamber, of the flow channel upper cover, and a second annular groove is formed in the end face, facing the flow channel upper cover, of the flow channel lower cover; the bottom of the first ring groove is provided with a first opening communicated to the second ring groove, and the bottom of the second ring groove is provided with a second opening communicated to the lower liquid chamber;
the end face, facing the runner lower cover, of the runner upper cover and the second annular groove jointly form the inertia channel.
Preferably, each pressure relief hole arranged on the decoupling film is annularly arranged on the decoupling film, and the shortest distance between each pressure relief hole and the side edge of the decoupling film is half of the shortest distance between each pressure relief hole and the central point of the decoupling film.
Preferably, each pressure relief hole arranged on the decoupling film is rounded.
Preferably, a step hole is formed in the flow channel lower cover, a boss matched with the step hole of the flow channel lower cover extends outwards from the outer edge of the decoupling film, the boss is lapped on the step of the step hole, and the boss is connected with the step of the step hole in a vulcanization mode.
Preferably, the powertrain hydraulic mount further comprises:
the rubber main spring and the aluminum core are vulcanized into a whole;
the upper end of the cylinder sleeve is fixedly vulcanized with the part of the rubber main spring;
the rubber sealing ring is integrally pressed with the lower end of the cylinder sleeve;
the runner assembly is pressed in the cylinder sleeve and is positioned between the rubber main spring and the rubber sealing ring;
the upper liquid chamber is formed between the rubber main spring and the flow channel assembly, and the lower liquid chamber is formed between the flow channel assembly and the rubber sealing ring.
Preferably, the end surface of the lower runner cover facing the upper runner cover is provided with a positioning boss in a protruding manner, and the end surface of the upper runner cover facing the lower runner cover is provided with a positioning hole matched with the positioning boss.
Preferably, an annular step is formed on the end face, facing the upper flow channel cover, of the lower flow channel cover, a mounting boss protrudes from the side wall of the annular step, the upper flow channel cover is buckled in the annular step, and a mounting groove matched with the mounting boss is formed in the upper flow channel cover to limit the movement of the upper flow channel cover in the circumferential direction.
The embodiment of the utility model provides a still provide an automobile, including foretell power assembly hydraulic pressure suspension.
The utility model has the advantages that:
because the sum of the cross-sectional areas of the pressure relief holes is far smaller than that of the inertia channel, most of liquid mainly flows through the inertia channel under the excitation of large amplitude such as a bumpy road and the like, and the characteristics of large rigidity and large damping are shown; meanwhile, a very small part of liquid flows through the pressure relief hole, so that the up-and-down movement of the decoupling film can be weakened, and the impact abnormal sound of the decoupling film and the flow channel assembly due to the up-and-down movement is reduced; under the excitation of small amplitude, most of liquid mainly flows through the pressure relief holes, the characteristic of small rigidity and small damping is shown, meanwhile, the up-and-down movement of the decoupling membrane can be weakened in the mode that the liquid flows through the pressure relief holes, and then the impact abnormal sound of the decoupling membrane and the runner assembly due to the up-and-down movement of the decoupling membrane is reduced.
Drawings
FIG. 1 is a schematic structural diagram of a floating decoupling membrane structure in the prior art;
FIG. 2 is a schematic structural diagram of a fixed decoupling membrane structure in the prior art;
fig. 3 is a schematic structural diagram of the cooperation of the flow channel assembly and the decoupling film in the present embodiment;
fig. 4 is a disassembled schematic view of the flow channel assembly and the decoupling film in the present embodiment;
FIG. 5 is a schematic structural diagram of a hydraulic mount of the powertrain in the present embodiment;
description of reference numerals: 11. a runner upper cover; 111. a first ring groove; 112. a first opening; 113. positioning holes; 114. installing a groove; 12. a runner lower cover; 121. a second ring groove; 122. a stepped bore; 123. positioning the boss; 124. an annular step; 125. mounting a boss; 2. a decoupling membrane; 21. a pressure relief vent; 22. a boss; 3. a liquid feeding chamber; 4. a lower liquid chamber; 5. a rubber main spring; 6. an aluminum core; 7. a cylinder liner; 8. a rubber seal ring; 9. a passive side cylinder.
Detailed Description
Exemplary embodiments of the present invention will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the invention are shown in the drawings, it should be understood that the invention can be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.
Referring to fig. 3 to 5, the utility model provides a power assembly hydraulic mount, include: the decoupling membrane 2 is arranged in the flow channel assembly; an inertia channel which is communicated with an upper liquid chamber 3 positioned above the flow channel assembly and a lower liquid chamber 4 positioned below the flow channel assembly is formed on the flow channel assembly; the decoupling film 2 is provided with at least two pressure relief holes 21 which are communicated with an upper liquid chamber 3 positioned above the flow channel assembly and a lower liquid chamber 4 positioned below the flow channel assembly; the ratio of the sum of the cross-sectional areas of the pressure relief holes 21 to the cross-sectional area of the inertia channel is 1: 14-1: 16.
The shape of the pressure relief hole 21 is not limited, and may be circular, oval, rectangular, or any other shape. In addition, in order to ensure that the stress of the decoupling film 2 is uniform and the reliability is improved, the number of the pressure relief holes 21 is generally not less than 3, and the pressure relief holes are preferably arranged uniformly in a circumference manner.
In the embodiment, as the sum of the cross-sectional areas of the pressure relief holes 21 is far smaller than that of the inertia channel, most of liquid mainly flows through the inertia channel under the excitation of large amplitude such as a bumpy road and the like, and the characteristic of large rigidity and large damping is shown; meanwhile, a very small part of liquid flows through the pressure relief hole 21, so that the up-and-down movement of the decoupling film 2 can be weakened, and the impact abnormal sound of the decoupling film 2 which moves up and down and the flow channel assembly is reduced; under the excitation of small amplitude, most of liquid mainly flows through the pressure relief holes 21, the characteristic of small rigidity and small damping is shown, meanwhile, the up-and-down movement of the decoupling membrane 2 can be weakened in the mode that the liquid flows through the pressure relief holes 21, and then the impact abnormal sound of the decoupling membrane 2 which moves up and down and is collided with the runner assembly is reduced.
As shown in fig. 3 and 4, the flow path assembly includes: the decoupling membrane comprises a runner upper cover 11 and a runner lower cover 12 which are oppositely arranged and fixedly connected, wherein an annular groove for mounting the decoupling membrane 2 is formed between the runner upper cover 11 and the runner lower cover 12; a first annular groove 111 is formed on the end surface of the flow channel upper cover 11 facing the upper liquid chamber 3, and a second annular groove 121 is formed on the end surface of the flow channel lower cover 12 facing the flow channel upper cover 11; the bottom of the first ring groove 111 is provided with a first opening 112 communicated to the second ring groove 121, and the bottom of the second ring groove 121 is provided with a second opening communicated to the lower liquid chamber 4; the end surface of the flow channel upper cover 11 facing the flow channel lower cover 12 and the second ring groove 121 together form the inertia channel.
The projection parts of the first opening 112 and the second opening in the axial direction of the decoupling film 2 are overlapped, and an inclined baffle plate is arranged on the flow channel upper cover 11, and the inclined baffle plate can block and guide the liquid passing through the first opening 112, so that the liquid cannot directly enter the lower liquid chamber 4 through the first opening 112, but flows through the second annular groove 121 for a circle under the guide of the inclined baffle plate through the first opening 112 and then flows into the lower liquid chamber 4 through the second opening.
As shown in fig. 3 and 4, a step hole 113 is formed in the flow channel lower cover 12, a boss 22 matched with the step hole 122 of the flow channel lower cover 12 extends outwards from the outer edge of the decoupling film 2, the boss 22 is lapped on the step of the step hole 122, and the boss 22 is connected with the step of the step hole 122 in a vulcanization manner.
As seen in fig. 4 and 5, the lower flow path cover 12 is provided with a stepped hole 113, a second annular groove 121, and an annular step 124 from the inside to the outside on the end surface facing the upper flow path cover 11. The step hole 122 is a through hole formed by connecting two holes with different diameters, wherein a boss 22 matched with the step of the step hole extends outwards from the outer wall of the decoupling film 2, part of the decoupling film 2 extends into one of the holes with smaller diameter in the step hole 113, the boss 22 is lapped on the step formed by the step hole 113, and the decoupling film 2 and the lower cover 12 of the flow channel are fixed by virtue of the step vulcanization of the boss 22 and the step hole. The second annular groove 121 and the end surface of the flow path upper cover 11 together form an inertial passage, so that the liquid flows from the upper liquid chamber 3 into the inertial passage through the first opening 112 and then flows from the second opening into the lower liquid chamber 4, or the liquid flows from the lower liquid chamber 4 into the inertial passage through the second opening and then flows from the first opening 112 into the upper liquid chamber 3.
Similarly, referring to fig. 4 and 5, the flow channel upper cover 11 has a through hole and a first annular groove 111 formed from inside to outside on the end surface thereof away from the flow channel lower cover 12. The bottom of the first ring groove 111 is further provided with a first opening 112 communicating with the second ring groove 121. The inner hole diameter of the flow path upper cover 11 is larger than the middle hole diameter of the stepped hole of the flow path lower cover 12, which is smaller in diameter. In this way, the boss 22 on the periphery of the decoupling film 2 is embedded between the step of the stepped hole and the end surface of the upper flow path cover 11 facing the lower flow path cover 12, and a certain gap is provided between the decoupling film 2 and the end surface of the upper flow path cover 11 facing the lower flow path cover 12. Therefore, the decoupling film 2 is vulcanized with the steps of the stepped hole through the bosses 22, the decoupling film 2 is connected with the runner lower cover 12 in the radial direction of the decoupling film 2, the decoupling film 2 cannot impact the runner lower cover 12 in the axial direction of the decoupling film, and the impact abnormal sound of the decoupling film 2 when the decoupling film passes through a deceleration strip or bumps can be thoroughly eliminated.
Preferably, in this embodiment, each of the pressure relief holes 21 provided in the decoupling film 2 is annularly provided in the decoupling film 2, and in order to ensure the rigidity of the middle position of the decoupling film 2, the shortest distance between each of the pressure relief holes 21 and the side edge of the decoupling film 2 is half of the shortest distance between each of the pressure relief holes 21 and the central point of the decoupling film 2, that is, the pressure relief hole 21 is arranged at about one-third of the outer side of the decoupling film 2.
In the present embodiment, in order to prevent stress concentration at the relief holes 21, the relief holes 21 provided in the decoupling film 2 are rounded.
As shown in fig. 4, preferably, a positioning boss 123 protrudes from an end surface of the lower flow channel cover 12 facing the upper flow channel cover 11, and a positioning hole 113 matched with the positioning boss 123 is provided on an end surface of the upper flow channel cover 11 facing the lower flow channel cover 12. The positioning hole 113 is in clearance fit with the positioning boss 123, and the radial movement of the lower runner cover 12 and the upper runner cover 11 is limited radially by the fit of the positioning boss 123 and the positioning hole 113.
As shown in fig. 4, an annular step 124 is formed on an end surface of the lower flow channel cover 12 facing the upper flow channel cover 11, a mounting boss 125 protrudes from a side wall of the annular step 124, the upper flow channel cover 11 is fastened in the annular step 124, and a mounting groove 114 matching with the mounting boss 125 is formed on the upper flow channel cover 11 to limit movement of the upper flow channel cover 11 in a circumferential direction. The runner upper cover 11 is integrally embedded in the annular step 124 after being assembled to the runner lower cover 12, and the top surface of the runner upper cover 11 is flush with the top surface of the runner knee.
As shown in fig. 5, the powertrain hydraulic mount further includes: a rubber main spring 5 and an aluminum core 6 which are vulcanized into a whole; the upper end of the cylinder sleeve 7 is vulcanized and fixed with the part of the rubber main spring 5; the rubber sealing ring 8 is integrally pressed with the lower end of the cylinder sleeve 7; the runner assembly is pressed in the cylinder sleeve 7 and is positioned between the rubber main spring 5 and the rubber sealing ring 8; the upper liquid chamber 3 is formed between the main rubber spring 5 and the flow path assembly, and the lower liquid chamber 4 is formed between the flow path assembly and the rubber seal 8.
The rubber main spring 5 is respectively connected with the aluminum core 6 and the cylinder sleeve 7 through vulcanization; the cylinder sleeve 7 is connected with the driven side cylinder body 9 in a riveting mode; the hydraulic suspension assembly of the power assembly can be completed by flanging the lower edge of the cylinder sleeve 7 and pressing the runner upper cover 11, the runner lower cover 12, the rubber sealing ring 8 and the cylinder sleeve 7 together.
The embodiment of the utility model provides a still provide an automobile, including foretell power assembly hydraulic pressure suspension.
Claims (9)
1. A powertrain hydraulic mount, comprising:
the decoupling membrane comprises a runner component and a decoupling membrane (2) arranged inside the runner component;
an inertia channel which is communicated with an upper liquid chamber (3) positioned above the flow channel assembly and a lower liquid chamber (4) positioned below the flow channel assembly is formed on the flow channel assembly;
the decoupling film (2) is provided with at least two pressure relief holes (21) which are communicated with an upper liquid chamber (3) positioned above the flow channel assembly and a lower liquid chamber (4) positioned below the flow channel assembly;
the ratio of the sum of the cross-sectional areas of the pressure relief holes (21) to the cross-sectional area of the inertia channel is 1: 14-1: 16.
2. The powertrain hydraulic mount of claim 1, wherein the flow channel assembly comprises:
the decoupling membrane decoupling device comprises a runner upper cover (11) and a runner lower cover (12) which are oppositely arranged and fixedly connected, wherein an annular groove for mounting the decoupling membrane (2) is formed between the runner upper cover (11) and the runner lower cover (12);
a first annular groove (111) is formed in the end face, facing the upper liquid chamber (3), of the flow channel upper cover (11), and a second annular groove (121) is formed in the end face, facing the flow channel upper cover (11), of the flow channel lower cover (12); a first opening (112) communicated to the second ring groove (121) is formed in the groove bottom of the first ring groove (111), and a second opening communicated to the lower liquid chamber (4) is formed in the groove bottom of the second ring groove (121);
the end face, facing the runner lower cover (12), of the runner upper cover (11) and the second annular groove (121) jointly form the inertia channel.
3. The powertrain hydraulic suspension of claim 1, characterized in that the pressure relief holes (21) provided on the decoupling membrane (2) are annularly arranged on the decoupling membrane (2), and the shortest distance between each pressure relief hole (21) and the side edge of the decoupling membrane (2) is half of the shortest distance between each pressure relief hole (21) and the center point of the decoupling membrane (2).
4. The powertrain hydraulic suspension of claim 1, characterized in that each of the pressure relief holes (21) provided on the decoupling membrane (2) is rounded.
5. The powertrain hydraulic suspension of claim 2, wherein a stepped hole (122) is formed in the lower flow passage cover (12), a boss (22) matched with the stepped hole (122) of the lower flow passage cover (12) extends outwards from the outer edge of the decoupling film (2), the boss (22) is lapped on the step of the stepped hole (122), and the boss (22) is connected with the step of the stepped hole (122) in a vulcanization mode.
6. The powertrain hydraulic mount of claim 1, further comprising:
a rubber main spring (5) and an aluminum core (6) which are vulcanized into a whole;
the upper end of the cylinder sleeve (7) is vulcanized and fixed with the part of the rubber main spring (5);
the rubber sealing ring (8) is integrally pressed with the lower end of the cylinder sleeve (7);
the runner assembly is pressed in the cylinder sleeve (7) and is positioned between the rubber main spring (5) and the rubber sealing ring (8);
the upper liquid chamber (3) is formed between the rubber main spring (5) and the flow channel assembly, and the lower liquid chamber (4) is formed between the flow channel assembly and the rubber sealing ring (8).
7. The powertrain hydraulic mount of claim 2, wherein the end surface of the runner lower cover (12) facing the runner upper cover (11) is provided with a positioning boss (123) in a protruding manner, and the end surface of the runner upper cover (11) facing the runner lower cover (12) is provided with a positioning hole (113) matched with the positioning boss (123).
8. The powertrain hydraulic mount of claim 2, wherein an end surface of the lower flow passage cover (12) facing the upper flow passage cover (11) is provided with an annular step (124), a mounting boss (125) protrudes from a side wall of the annular step (124), the upper flow passage cover (11) is buckled in the annular step (124), and a mounting groove (114) matched with the mounting boss (125) is formed in the upper flow passage cover (11) to limit the movement of the upper flow passage cover (11) in the circumferential direction.
9. An automobile comprising a powertrain hydraulic mount of any of claims 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021237828.6U CN212643402U (en) | 2020-06-30 | 2020-06-30 | Power assembly hydraulic suspension and car |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021237828.6U CN212643402U (en) | 2020-06-30 | 2020-06-30 | Power assembly hydraulic suspension and car |
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| Publication Number | Publication Date |
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| CN212643402U true CN212643402U (en) | 2021-03-02 |
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| CN202021237828.6U Active CN212643402U (en) | 2020-06-30 | 2020-06-30 | Power assembly hydraulic suspension and car |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113915287A (en) * | 2021-10-25 | 2022-01-11 | 建新赵氏科技有限公司 | Hydraulic suspension decoupling vibration isolation device |
| CN114992272A (en) * | 2022-06-20 | 2022-09-02 | 重庆长安汽车股份有限公司 | Hydraulic suspension and car |
-
2020
- 2020-06-30 CN CN202021237828.6U patent/CN212643402U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113915287A (en) * | 2021-10-25 | 2022-01-11 | 建新赵氏科技有限公司 | Hydraulic suspension decoupling vibration isolation device |
| CN114992272A (en) * | 2022-06-20 | 2022-09-02 | 重庆长安汽车股份有限公司 | Hydraulic suspension and car |
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