CN217898627U

CN217898627U - Engine hydraulic suspension

Info

Publication number: CN217898627U
Application number: CN202222133689.8U
Authority: CN
Inventors: 杨洋; 谷玉山
Original assignee: Great Wall Motor Co Ltd
Current assignee: Great Wall Motor Co Ltd
Priority date: 2022-08-14
Filing date: 2022-08-14
Publication date: 2022-11-25
Anticipated expiration: 2032-08-14

Abstract

The utility model provides an engine hydraulic pressure suspension, this hydraulic pressure suspension include casing, main spring subassembly and leather cup subassembly, wherein, hold the intracavity between main spring subassembly and leather cup subassembly, accept to hold the chamber and separate the runner plate for last cavity and lower cavity. The runner plate is provided with a decoupling film and a runner communicating the upper chamber with the lower chamber, and also comprises an upper runner plate and a lower runner plate, and an elastic piece is supported between the upper runner plate and the lower runner plate. The cup assembly is screwed in the shell with adjustable screwing depth, and the screwing depth of the cup assembly in the shell is adjusted to drive the lower runner plate to be close to or far away from the upper runner plate. The utility model discloses an engine hydraulic pressure suspension through the leather cup subassembly that sets up, after hydraulic pressure suspension whole equipment finishes, also can close the mode of the degree of depth soon in the casing with changing the leather cup subassembly, orders about down the flow passage board and is close to or keeps away from the up flow passage board to the clearance of adjustment runner, thereby carries out the adjustment of hydraulic pressure suspension's damping.

Description

Engine hydraulic suspension

Technical Field

The utility model relates to an automobile parts technical field, in particular to engine hydraulic pressure suspension.

Background

Along with the improvement of living standard of people, people have higher and higher requirements on the comfort of riding automobiles. The powertrain suspension system plays a crucial role in improving the ride comfort and reducing noise of the vehicle.

The liquid flow in the hydraulic suspension can generate damping, and the damping of the hydraulic suspension plays an important role in reducing the vibration of the automobile. The hydraulic suspension is a bidirectional vibration isolation element which is used for connecting and supporting a power assembly and has restraining and protecting effects on movement tendency. The existing suspension types mainly comprise rubber suspension, hydraulic suspension, semi-active suspension, active suspension and the like. In use, the suspension functions primarily include securing and supporting the vehicle powertrain, bearing the reciprocating inertial forces and moments generated within the powertrain by the rotating and translating masses of the engine, bearing all dynamic forces acting on the powertrain during vehicle operation, isolating frame or body vibrations caused by engine excitation, and isolating the transfer of body vibrations to the powertrain caused by road surface irregularities and wheel impacts.

Although the application of the suspension structure can bring great benefits to the good operation of an automobile body, particularly a power assembly, the damping of the hydraulic suspension cannot be adjusted according to the specific automobile condition of the automobile after the suspension at the present stage is installed, so that the adaptability to different working condition environments of the automobile is poor, and certain limitations exist.

SUMMERY OF THE UTILITY MODEL

In view of this, the utility model aims at providing an engine hydraulic mount to improve the unable adjustment's of current hydraulic mount damping after being the finished product problem.

In order to achieve the above purpose, the technical scheme of the utility model is realized like this:

a hydraulic suspension of an engine comprises a shell, a main spring component and a leather cup component which are arranged in the shell in a sealing way along the axial direction of the shell, a runner plate which divides an accommodating cavity into an upper cavity and a lower cavity is accommodated in the accommodating cavity between the main spring component and the leather cup component, the runner plate is provided with a decoupling film and a runner which is communicated with the upper cavity and the lower cavity,

the flow passage plate comprises an upper flow passage plate and a lower flow passage plate which are attached along the axial direction of the shell, and an elastic piece is supported between the upper flow passage plate and the lower flow passage plate;

the cup assembly is screwed in the shell, and the screwing depth is adjustable so as to drive the lower runner plate to be close to or far away from the upper runner plate.

Further, the packing cup subassembly includes: the rotary joint body is screwed in the shell, and an operating part is formed at the bottom of the rotary joint body so as to drive the rotary joint body to be screwed in or out of the shell; and the leather cup is fixedly connected to the top of the rotary connection body.

Further, the operating portion is configured as a hexagonal counterbore formed at the bottom of the swivel body.

Furthermore, the outer surface of the lower part of the shell is distributed with a mark part; an indicating part for indicating the marking part is arranged on the bottom surface of the rotary connection body.

Further, the indicating portion is configured as an indicating arrow pointing to the marking portion.

Further, the elastic member is configured as a spring supported between the upper flow field plate and the lower flow field plate.

Furthermore, clamping grooves for embedding the springs are formed on the surfaces, opposite to each other, of the upper flow passage plate and the lower flow passage plate.

Furthermore, a positioning mechanism which guides the upper flow channel plate and the lower flow channel plate to be jointed in a plug-in fit manner is arranged between the upper flow channel plate and the lower flow channel plate.

Further, the flow path includes: a decoupling flow channel including a first high-frequency flow channel hole formed through the upper flow channel plate and a second high-frequency flow channel hole formed through the lower flow channel plate, the first high-frequency flow channel hole and the second high-frequency flow channel hole being disposed in correspondence with each other in an axial direction of the housing; the decoupling film is provided between the upper flow path plate and the lower flow path plate in a floating manner, and covers the first high-frequency flow path hole and the second high-frequency flow path hole.

Further, the flow path includes: the inertial flow passage comprises a first low-frequency flow passage hole formed in the upper flow passage plate in a penetrating manner, a second low-frequency flow passage hole formed in the lower flow passage plate in a penetrating manner, and an inertial passage for communicating the first low-frequency flow passage hole with the second low-frequency flow passage hole under the state that the upper flow passage plate and the lower flow passage plate are attached.

The utility model discloses an engine hydraulic pressure suspension, through the leather cup subassembly that sets up, after hydraulic pressure suspension whole equipment finishes, also can order about down the flow path board near or keep away from the runner board with the mode that changes the leather cup subassembly and close the degree of depth soon in the casing to the clearance of adjustment runner, thereby carry out the adjustment of hydraulic pressure suspension damping size.

In addition, the operating part is arranged and is constructed into the hexagonal counter bore formed at the bottom of the screwing body, so that the screwing depth of the leather cup assembly can be conveniently adjusted from the outside.

In addition, through the arranged marking part and the indication part, the reference can be provided for the rotation angle of the screwing body; and then be convenient for control this hydraulic suspension's damping more accurately.

Drawings

The accompanying drawings, which form a part of the present disclosure, are provided to provide a further understanding of the present disclosure, and the exemplary embodiments and descriptions thereof are provided to explain the present disclosure, wherein the related terms in the front, back, up, down, and the like are only used to represent relative positional relationships, and do not constitute an undue limitation of the present disclosure. In the drawings:

fig. 1 is a schematic diagram of an internal structure of a hydraulic mount of an engine according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of a housing of an engine hydraulic mount according to an embodiment of the present invention;

fig. 3 is a schematic structural view of an upper runner plate of an engine hydraulic mount according to an embodiment of the present invention;

fig. 4 is a schematic structural diagram of a lower flow channel plate of an engine hydraulic mount according to an embodiment of the present invention;

fig. 5 is a schematic structural diagram of a decoupling film of an engine hydraulic mount according to an embodiment of the present invention;

fig. 6 is a schematic structural diagram of a swivel body of an engine hydraulic mount according to an embodiment of the present invention;

fig. 7 is a schematic structural diagram of a seal ring of an engine hydraulic mount according to an embodiment of the present invention;

fig. 8 is a schematic structural diagram of a cup for hydraulic suspension of an engine according to an embodiment of the present invention.

Description of reference numerals:

1. a housing; 11. a marking section; 12. a flange; 13. mounting holes; 14. reinforcing ribs;

21. main spring rubber; 22. a main spring skeleton;

31. a leather cup; 32. a swivel body; 321. a hexagonal counter bore; 322. an indicating section; 33. a seal ring;

42. an upper flow path plate; 43. a lower flow field plate; 44. an upper chamber; 45. a lower chamber; 46. a decoupling membrane; 461. a protrusion; 47. an elastic member; 481. a card slot; 491. positioning a bolt; 492. positioning the socket; 493. a flow channel ridge; 494a, a first high-frequency flow channel hole; 494b, a second high-frequency flow channel hole; 495a, a first low frequency runner hole; 495b, second low frequency flow channel hole.

Detailed Description

It should be noted that, in the case of no conflict, the embodiments and features of the embodiments of the present invention may be combined with each other.

In the description of the present invention, it should be noted that if terms indicating directions or positional relationships such as "up", "down", "inside", "outside", etc. appear, they are based on the directions or positional relationships shown in the drawings, and are only for convenience of description of the present invention and simplification of description, but do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and thus, should not be construed as limiting the present invention. Furthermore, the appearances of the terms first, second, etc. in this specification are not necessarily all referring to the same order, but are to be construed as referring to the same order.

In addition, in the description of the present invention, the terms "mounted," "connected," and "connecting" are to be construed broadly unless otherwise specifically limited. For example, the connection may be fixed, detachable, or integrated; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. To those of ordinary skill in the art, the specific meaning of the above terms in the present invention can be understood in combination with the specific situation.

The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

The embodiment relates to an engine hydraulic mount, and an exemplary structure of the engine hydraulic mount is shown in fig. 1 and fig. 2.

Overall, the engine hydraulic mount of the present embodiment mainly includes a housing 1, a main spring assembly, and a cup assembly. The hydraulic mount of the engine forms the adjustment of the damping magnitude of the hydraulic mount by adjusting the screwing depth of the leather cup assembly in the shell 1.

Based on the above overall design concept, in one embodiment of the present embodiment, as shown in fig. 1, specifically, the cup assembly is hermetically disposed in the casing 1 along the axial direction of the casing 1, and a runner plate that divides the chamber into an upper chamber 44 and a lower chamber 45 is accommodated in the chamber between the main spring assembly and the cup assembly. The flow path plate has a decoupling film 46, and is provided with a flow path communicating the upper chamber 44 and the lower chamber 45. The flow path plate further includes an upper flow path plate 42 and a lower flow path plate 43 which are disposed in contact with each other in the axial direction of the housing 1, and an elastic member 47 having a structure such as a spring is supported between the upper flow path plate 42 and the lower flow path plate 43.

As set forth above, the cup assembly can drive the lower runner plate 43 to approach or separate from the upper runner plate 42 by the operation of external force to change the screwing depth of the cup assembly with the housing 1. Resulting in an adjustment of the amount of damping of the hydraulic mount of the present embodiment.

As for the housing 1, as shown in fig. 2, it is provided with mounting holes 13 for facilitating the mounting of the present hydraulic mount on a vehicle. Further, a flange 12 is formed on the housing 1, and a mounting hole 13 is formed in the flange 12. In addition, a reinforcing rib 14 is further provided between the flange 12 and the housing 1, which is beneficial to making the installation of the hydraulic mount of the embodiment on the vehicle more stable while enhancing the structural strength of the housing 1 itself.

In the case of the main spring assembly, which includes a main spring rubber 21 and a main spring frame 22 provided inside the case 1, an inner core is vulcanization molded in the main spring rubber 21. The main spring frame 22 is also molded inside the main spring rubber 21. So that the main spring rubber 21 has better structural performance. For the main spring assembly, it is well known in the art and is not the main content of the embodiment, so the detailed description thereof is omitted.

As shown in fig. 6 to 8, the cup assembly includes a screw body 32 having a bottom portion configured with an operation portion, and a cup 31 fixedly connected to a top portion of the screw body 32.

The operation portion can be provided with an inner hexagonal counter bore 321 for facilitating manual operation, and of course, other forms such as a quadrangular counter bore or a straight counter bore are also possible.

Further, a seal ring 33 as shown in fig. 7 is provided at a portion where the screw body 32 and the housing 1 are in contact with each other, to solve a problem that sealability may be lowered by adjusting a screwing depth.

As for the cup 31, in order to improve the problem that abnormal noise is easily generated when the structure of the swivel body 32 and the runner plate in the hydraulic mount are directly or indirectly contacted, in the embodiment, compared with the conventional arrangement in the art, the shape of the cup 31 is as shown in fig. 8, and an annular protrusion is provided.

In addition, in order to make the adjustment process of adjusting the damping magnitude more accurate and controllable, in the present embodiment, the mark portions 11 are distributed in the circumferential direction of the outer surface of the housing 1 where the screw body 32 is located. As shown in fig. 1 and fig. 6, an indication portion 322 for indicating the marking portion 11 is further provided on the bottom surface of the screw body 32.

The mark part 11 is provided as a scale protrusion, and the indication part 322 is provided as an indication arrow. After the screw-on body 32 is mounted on the housing 1, the scale indicated by the arrow before the suspension damping state is adjusted is used as a zero scale, and then the zero scale is used as a reference, so as to adjust the damping.

The suspension damper of this embodiment is such that the spring members 47 supporting the upper and lower

flow field plates

42, 43 are constantly energized during operation to bias the upper and lower

flow field plates

42, 43 away from each other. Also, the elastic member 47 is generally provided as a spring. Correspondingly, the ring-shaped spring locking groove 481 shown in fig. 3 and 4 is formed on both the upper flow field plate 42 and the lower flow field plate 43.

In the present embodiment, in order to facilitate the assembly between the upper flow field plate 42 and the lower flow field plate 43, a positioning mechanism for guiding the upper flow field plate 42 and the lower flow field plate 43 to be attached in a plug-in fit manner is provided between the upper flow field plate 42 and the lower flow field plate 43. Specifically, as shown in fig. 3 in combination with fig. 4, the upper flow path plate 42 is provided with a positioning socket 492, and the lower flow path plate 43 is provided with a positioning pin 491.

For the upper flow field plate 42 and the lower flow field plate 43, low frequency flow field holes are provided. The low frequency flow path holes include a second low frequency flow path hole 495b formed in the lower flow path plate 43 and a first low frequency flow path hole 495a formed in the upper flow path plate 42, respectively.

Specifically, a flow channel ridge 493 forming an inertial flow channel is formed on the lower flow channel plate 43, and a second low-frequency flow channel hole 495b is formed in the lower flow channel plate 43 at one end of the flow channel ridge 493; accordingly, the upper flow path plate 42 is provided with a first low frequency flow path hole 495a. When the upper flow passage plate 42 and the lower flow passage plate 43 are fitted to each other, the flow passage ridges 493 of the upper flow passage plate 42 and the lower flow passage plate 43 form an inertial flow passage, and liquid in the hydraulic mount enters and exits the inertial flow passage through the low-frequency flow passage holes. Therefore, the hydraulic suspension of the automobile is convenient to damp and buffer the engine under the low-frequency vibration of the engine.

In addition, the flow passage also comprises a decoupling flow passage. The decoupling flow path includes high frequency flow path holes formed through the upper flow path plate 42 and the lower flow path plate 43. Specifically, the high-frequency runner holes include a first high-frequency runner hole 494a formed in the upper runner plate 42 and a second high-frequency runner hole 494b formed through the lower runner plate 43. In the axial direction of the housing 1, the first high-frequency flow passage hole 494a and the second high-frequency flow passage hole 494b are provided correspondingly; the decoupling film 46 is provided floating between the upper flow field plate 42 and the lower flow field plate 43, and covers the first high-frequency flow field hole 494a and the second high-frequency flow field hole 494b.

Further, similarly to the cup 31, in order to improve the problem that the upper flow path plate 42 and the lower flow path plate 43 easily collide with each other during operation and thus generate abnormal noise, a protrusion 461 shown in fig. 5 is provided on the decoupling film 46. Of course, the protrusion 461 may be in the shape of a ring, a raised stripe, a bump, or the like, so as to prevent a hard collision between the upper flow path plate 42 and the lower flow path plate 43.

In the hydraulic mount of the engine of the embodiment, through the arrangement of the cup assembly, after the hydraulic mount is integrally assembled, the screwing depth of the cup assembly in the housing 1 can be changed, for example, as the screwing body 32 is changed from a completely-pressed state of pressing the lower flow passage plate 43 into a completely-unscrewed state in the housing 1, the distance between the upper flow passage plate 42 and the lower flow passage plate 43 is continuously increased under the action of the elastic element 47; the distance between the decoupling film 46 and the upper flow channel plate 42 and the lower flow channel plate 43 is increased, and further, the flow resistance of the liquid in the hydraulic mount of the embodiment is correspondingly reduced in a high-frequency state, so that the damping is reduced, and the buffering effect of the hydraulic mount of the engine on the high-frequency vibrating engine is improved.

In addition, the operation part provided with the hexagonal counterbore 321 is used for facilitating the adjustment of the damping size of the engine hydraulic suspension after the engine hydraulic suspension is assembled. The mark part 11 and the indication part 322 can make the damping adjustment process more accurate.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and should not be construed as limiting the scope of the present invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the present invention.

Claims

1. The utility model provides an engine hydraulic suspension, includes casing (1), follows the axial seal of casing (1) arranges main spring subassembly and leather cup subassembly in casing (1) main spring subassembly with in the appearance chamber between the leather cup subassembly, accept with hold the chamber and separate the runner board for last cavity (44) and lower cavity (45), the runner board has decoupling zero membrane (46) and intercommunication go up cavity (44) with the runner of cavity (45) down, its characterized in that:

the runner plate comprises an upper runner plate (42) and a lower runner plate (43) which are arranged along the axial direction of the shell (1) in an attaching mode, and an elastic piece (47) is arranged between the upper runner plate (42) and the lower runner plate (43) in a supporting mode;

the cup assembly is screwed in the shell (1), and the screwing depth is adjustable so as to drive the lower runner plate (43) to be close to or far away from the upper runner plate (42).

2. The engine hydraulic mount of claim 1, wherein the cup assembly comprises:

the screwing body (32) is screwed in the shell (1), and an operating part is formed at the bottom of the screwing body (32) to drive the screwing body (32) to screw in or out the shell (1);

and the leather cup (31) is fixedly connected to the top of the rotary connection body (32).

3. The engine hydraulic mount of claim 2, wherein: the operating portion is configured as a hexagonal counterbore (321) formed at the bottom of the swivel body (32).

4. The engine hydraulic mount of claim 2, wherein: the outer surface of the lower part of the shell (1) is distributed with a mark part (11); an indication part (322) for indicating the marking part (11) is arranged on the bottom surface of the screwing body (32).

5. The engine hydraulic mount of claim 4, wherein: the indicator (322) is configured as an indicator arrow pointing to the marking (11).

6. The engine hydraulic mount of claim 1, wherein: the elastic member (47) is configured as a spring supported between the upper flow field plate (42) and the lower flow field plate (43).

7. The engine hydraulic mount of claim 6, wherein: on the surfaces of the upper flow path plate (42) and the lower flow path plate (43) which are arranged oppositely, a clamping groove (481) for embedding the spring is formed respectively.

8. The engine hydraulic mount of claim 1, wherein: and a positioning mechanism which guides the upper runner plate (42) and the lower runner plate (43) to be jointed in a plug-in fit manner is arranged between the upper runner plate (42) and the lower runner plate (43).

9. The engine hydraulic mount of any of claims 1-8, wherein the flow passage comprises:

a decoupling flow path including a first high-frequency flow path hole (494 a) formed through the upper flow path plate (42) and a second high-frequency flow path hole (494 b) formed through the lower flow path plate (43), the first high-frequency flow path hole (494 a) and the second high-frequency flow path hole (494 b) being disposed in correspondence with each other in the axial direction of the housing (1); the decoupling film (46) is provided in a floating manner between the upper flow field plate (42) and the lower flow field plate (43), and covers the first high-frequency flow field hole (494 a) and the second high-frequency flow field hole (494 b).

10. The engine hydraulic mount of claim 9, wherein the flow passage comprises:

the inertial flow channel comprises a first low-frequency flow channel hole (495 a) formed in the upper flow channel plate (42) in a penetrating manner, a second low-frequency flow channel hole (495 b) formed in the lower flow channel plate (43) in a penetrating manner, and an inertial channel which is communicated with the first low-frequency flow channel hole (495 a) and the second low-frequency flow channel hole (495 b) under the attaching state of the upper flow channel plate (42) and the lower flow channel plate (43).