CN210510095U

CN210510095U - Hydraulic damping piston and hydraulic damper giving consideration to side inclination and vibration of automobile

Info

Publication number: CN210510095U
Application number: CN201921025665.2U
Authority: CN
Inventors: 郭怀宝; 陈群燕; 韩道刚; 王卫海
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-07-03
Filing date: 2019-07-03
Publication date: 2020-05-12
Anticipated expiration: 2029-07-03

Abstract

A hydraulic damping piston and a hydraulic damper for both side inclination and vibration of an automobile belong to the technical field of hydraulic damping. Including piston cylinder (2), piston rod (1) drive piston body (4) axial or/and circumferential movement in piston cylinder (2), its characterized in that: a throttling groove (3) is formed in the inner wall of the piston cylinder (2), and a circulation channel of hydraulic oil is formed between the piston body (4) and the throttling groove (3) at intervals; the thickness of the longitudinal section of the piston body (4) is increased in sequence. In this compromise car heels and the hydraulic shock piston and the hydraulic shock absorber of vibrations, adjust throttle groove and diversion through setting up the shock attenuation and adjust the recess, play the buffering when the car violently shakes and heels because of the diversion arouses, avoided the automobile body to damage and guaranteed personal safety, improved the security and the nature controlled of driving simultaneously.

Description

Hydraulic damping piston and hydraulic damper giving consideration to side inclination and vibration of automobile

Technical Field

A hydraulic damping piston and a hydraulic damper for both side inclination and vibration of an automobile belong to the technical field of hydraulic damping.

Background

Hydraulic damping is a common damping mode in the field of automobiles. The output end and the body of the automobile hydraulic shock absorber are respectively arranged on the automobile body and the wheel assembly, and the automobile hydraulic shock absorber mainly plays a role in buffering when the automobile body and a tire (namely the ground) move relatively to each other by a large extent, so that the driving safety and the comfort are improved.

The automobile body vibration caused by the fact that an automobile body touches an obstacle or wheels suddenly sink into a pit in the running process of an automobile is the most common state that relative movement occurs between the automobile body and the wheels in the running process of the automobile, and is also the most common situation of application of a hydraulic shock absorber. However, in the prior art, the design of the hydraulic shock absorber for the automobile usually only focuses on the buffering effect of the automobile when the automobile body vibrates, and often ignores another situation that the automobile body and the wheels move relatively, which is easily caused in the running process of the automobile, namely that the automobile changes direction, and especially the automobile body rolls caused by changing direction at high speed in an emergency situation of the automobile.

Because the output end and the body of the automobile hydraulic shock absorber are respectively arranged on the automobile body and the wheels, when the automobile is turned to cause heeling, the shock absorber piston in part of automobile shock absorbers (such as Macpherson suspension) can not only axially move relative to the piston cylinder, but also can rotate relative to the piston cylinder, so that the working state of the automobile shock absorber when the automobile body heels is more complicated, and the heeling condition caused by turning of the automobile can not be ignored when the automobile hydraulic shock absorber is designed.

When the automobile is emergently turned, the relative movement and rotation amplitude between the piston and the piston cylinder is in direct proportion to the turning speed of the automobile, so that the distance between an automobile body and wheels is rapidly changed in a short time when the automobile is emergently turned, the piston is still adjusted according to the inherent state under the condition, the automobile body is easily turned over, the automobile body is inclined due to turning, the greater potential safety hazard is caused, the automobile body is damaged, and casualties can be directly caused. Therefore, it is an urgent problem to design a hydraulic shock absorber for an automobile, which not only has a shock absorbing effect, but also has a shock absorbing effect on the side inclination of the automobile body.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is: the hydraulic damping piston and the hydraulic damper overcome the defects of the prior art, and the hydraulic damping piston and the hydraulic damper have the advantages that the hydraulic damping piston and the hydraulic damper are provided with the throttling groove and the turning adjusting groove, the automobile strongly vibrates and the automobile tilts due to turning, the automobile body is prevented from being damaged, and the personal safety is guaranteed.

The utility model provides a technical scheme that its technical problem adopted is: this compromise hydraulic damping piston that car heeled and vibrations, including the piston barrel that is full of hydraulic oil, be provided with the piston body in the piston barrel, the piston body is connected to piston rod one end, and the other end is drawn forth from the piston barrel port, and the piston rod drives the piston body at piston barrel axial reciprocating motion or/and with piston barrel circumference reciprocating rotation, its characterized in that: the inner wall of the piston cylinder is provided with a throttling groove, the outer wall of the piston body is attached to the throttling groove, and a circulation channel of hydraulic oil is formed at the attachment surface at intervals;

when the piston body rotates in the inner circumference direction of the piston cylinder in a reciprocating mode, the joint position of the throttling groove and the outer wall of the piston body changes between the thinnest position and the thickest position of the piston body in a reciprocating mode, and the length of a circulation channel at the joint face changes.

Preferably, at least one group of throttling grooves is formed in the inner wall of the piston cylinder along the axial direction of the piston cylinder.

Preferably, the throttling groove comprises a flow equalizing section and a throttling section, the flow equalizing section is a groove with uniform depth, the throttling section extends from two ends of the flow equalizing section to two outer sides, and the throttling section is a slope-shaped groove with deep inside and shallow outside; the axial length of the flow equalizing section is longer than the thickness of the piston body.

Preferably, the upper part or/and the lower part of the piston body is/are provided with a radial through diversion adjusting groove, the heights of the groove walls of the diversion adjusting groove are sequentially increased from the center to the two sides, and the groove walls of the diversion adjusting groove and the throttling groove are in reciprocating staggered with each other along with the circumferential reciprocating rotation of the piston body and the piston cylinder.

Preferably, the upper part or/and the lower part of the piston body is/are provided with arc-shaped bulges, and the upper edges and the lower edges of the bulges are respectively the maximum part and the minimum part of the thickness of the piston body.

Preferably, the throttling section of the throttling groove is in a multi-section type, the throttling section is divided into a plurality of sections from the inner side to the outer side of the throttling groove, and the depth of each section is reduced in sequence.

Preferably, the cross section of the turning adjusting groove is arc-shaped, and the groove wall of the turning adjusting groove is an arc line which is sequentially lifted from the center to two sides.

Preferably, the cross section of the direction-changing adjusting groove is triangular, and the groove wall of the direction-changing adjusting groove is a straight line which sequentially rises from the center to two sides.

Preferably, the longitudinal section of the piston body is in a right trapezoid shape,

the utility model provides a compromise hydraulic shock absorber that car heeled and vibrations which characterized in that: the outer side of the piston cylinder is hermetically sleeved with a shock absorber outer cylinder, an outer oil cavity of the shock absorber is formed between the shock absorber outer cylinder and the piston cylinder at intervals, and the bottom of the piston cylinder is communicated with the shock absorber outer cylinder.

Compared with the prior art, the utility model discloses the beneficial effect who has is:

in this compromise car heels and the hydraulic shock piston and the hydraulic shock absorber of vibrations, adjust throttle groove and diversion through setting up the shock attenuation and adjust the recess, play the buffering when the car violently shakes and heels because of the diversion consequently, avoided the automobile body to damage and guaranteed personal safety, improved the security and the nature controlled of driving simultaneously.

When great vibrations take place between automobile body and the wheel assembly, this realization of piston can take place to remove by a wide margin in the piston intracavity under the drive of piston rod, moves the throttle section in the throttle groove to vibrations gradually, because the degree of depth of throttle section reduces in proper order, consequently along with the piston body removes to the end in the piston intracavity, and the area that flows of throttle groove is adjusted with piston body complex vibrations is littleer and smaller, has consequently played the effect that slows down the shock attenuation degree.

When the automobile changes direction, after the piston body and the throttling groove rotate relatively, under the action of groove walls on two sides of the direction-changing adjusting groove, the thickness of the piston body forming a circulation channel with the throttling groove at intervals is gradually increased, namely, the circulation length of hydraulic oil is prolonged, so that the flow speed of the hydraulic oil between the piston bodies is reduced, the hydraulic shock absorption is hardened, and the automobile body is prevented from tilting to the greatest extent.

And if the vehicle speed is too fast or the turning angle is large, the centrifugal force caused by the turning of the vehicle body can still overcome the hydraulic damping piston to roll, and at the moment, the piston body and the piston cylinder can still axially move relatively, namely the piston body and the throttling groove can further adjust the hydraulic damping piston according to the roll of the vehicle body. The piston body firstly can move in the length range of the flow equalizing section in the throttling groove and gradually moves to the throttling section in the throttling groove, and the depth of the throttling section is reduced in sequence, so that the piston body moves towards the end in the piston cavity, namely the flow area of hydraulic oil is smaller and smaller, and the effect of preventing the car body from tilting is further achieved through the cooperation of the piston body and the throttling groove.

Drawings

Fig. 1 is a schematic structural view of an embodiment 1 of a hydraulic damping piston for achieving both roll and vibration of an automobile.

Fig. 2 is a side view of fig. 1.

Fig. 3 is a schematic view of an embodiment 1 of a hydraulic damping piston for balancing the roll and vibration of the automobile in a turning state of the automobile.

Fig. 4 is a schematic structural view of the hydraulic shock absorber.

Fig. 5 is a schematic structural view of embodiment 2 of a hydraulic damping piston for achieving both roll and vibration of an automobile.

Fig. 6 is a schematic structural view of embodiment 3 of the hydraulic damping piston for achieving both roll and vibration of the automobile.

Fig. 7 is a schematic structural view of embodiment 4 of a hydraulic damping piston for achieving both roll and vibration of an automobile.

Wherein: 1. the piston rod 2, the piston cylinder 3, the throttling groove 4, the piston body 5, the turning adjusting groove 6 and the outer cylinder of the shock absorber.

Detailed Description

Fig. 1 to 4 are preferred embodiments of the present invention, and the present invention will be further explained with reference to fig. 1 to 7.

Example 1:

as shown in fig. 1-2, a hydraulic damping piston for both side tilting and vibration of an automobile comprises a piston cylinder 2, wherein the piston cylinder 2 is a cylinder with two closed ends, an inner cavity of the piston cylinder 2 is a piston cavity, and hydraulic oil is filled in the piston cavity. A piston body 4 is arranged in the piston cavity, the piston body 4 is in close contact with the inside of the piston cavity, and the piston cavity is divided into an upper oil cavity and a lower oil cavity. One end of the piston rod 1 is connected to the center of the piston body 4, the other end of the piston rod is led out from any end of the piston cylinder 2, and the piston body 4 is driven by the piston rod 1 to axially reciprocate in the piston cavity.

Two throttling grooves 3 are axially formed in the inner wall of the piston cylinder 2, the two throttling grooves 3 are symmetrically formed in the radial direction of the piston cylinder 2, each throttling groove 3 comprises a flow equalizing section in the center and throttling sections located on two sides of the flow equalizing section, the flow equalizing section is defined as the initial position of the piston body 4 in axial reciprocating motion, the axial length of the flow equalizing section is longer than the thickness of the piston body 4, and the flow equalizing section is a groove with uniform depth. The throttling section extends from the outer end surface of the flow equalizing section to the outer side of the corresponding end respectively, and the depth of the throttling section is reduced in sequence to form a slope-shaped groove.

Turning adjusting groove 5 has been seted up along piston body 4's radial on piston body 4's upper portion, and turning adjusting groove 5 is the penetrating groove that radially pierces through piston body 4, and in this embodiment, 5 cross-sections of turning adjusting groove are the arc, and the cell wall of turning adjusting groove 5 is the pitch arc that risees in proper order to both sides from the center promptly.

Because the piston cylinder 2 and the piston body 4 rotate relatively when the automobile turns, when the automobile runs straight, the relative position between the piston cylinder 2 and the piston body 4 is recorded as the initial position of the relative rotation, and the opening direction of the turning adjusting groove 5 is perpendicular to the connecting line of the two throttling grooves 3 at the initial position.

The specific working process and working principle are as follows:

the piston rod 1 and the piston cylinder 2 are respectively fixed on the automobile body and the wheel assembly of the automobile, when the automobile is in a straight-line running state, slight vibration occurs on the automobile body and the wheel assembly, only axial relative movement can occur between the piston rod 1 and the piston cylinder 2, at the moment, the piston body 4 moves in the length range of the flow equalizing section in the throttling groove 3, the piston body 4 moves in the moving process, hydraulic oil in a piston cavity can flow from one side of the piston body 4 to the other side of the piston cavity through the throttling groove 3, the flow area of the hydraulic oil in the process of flowing through the throttling groove 3 is limited by the throttling groove 3, the moving speed of the piston body 4 is reduced, and therefore the damping effect is achieved.

When great vibrations take place between automobile body and the wheel assembly, piston body 4 can take place to remove by a wide margin in the piston intracavity under the drive of piston rod 1, moves the throttle section in the throttle groove 3 gradually, because the degree of depth of throttle section reduces in proper order, consequently along with piston body 4 removes to the end in the piston intracavity, and the area that flows of hydraulic oil is littleer and more promptly, has consequently played the effect that slows down the shock attenuation degree.

Referring to fig. 3, when the automobile changes direction, the piston body 4 is driven by the piston rod 1 to rotate axially with the piston cylinder 2, which further causes the direction-changing adjusting groove 5 and the throttling grooves 3 to rotate relatively and then to be staggered, because at the initial position of the relative rotation, the opening direction of the direction-changing adjusting groove 5 is perpendicular to the connecting line of the two throttling grooves 3, that is, the thinnest part of the piston body 4 (the lowest part of the direction-changing adjusting groove 5) and the throttling grooves 3 form a flow channel of hydraulic oil at intervals, and after the piston body 4 and the throttling grooves 3 rotate relatively, under the effect of the groove walls at the two sides of the direction-changing adjusting groove 5, the thickness of the piston body 4 forming the flow channel with the throttling grooves 3 at intervals is gradually increased, that is, the flow length of the hydraulic oil is prolonged, thereby slowing down the flow speed between the piston bodies 4, and hardening the hydraulic damping piston, the vehicle body is prevented from rolling to the maximum extent.

And if the vehicle speed is too fast or the turning angle is large, the centrifugal force caused by the turning of the vehicle body can still overcome the hydraulic damping piston to roll, and at the moment, the piston body 4 and the piston cylinder 2 can also axially move relatively, namely, the hydraulic damping piston can be further adjusted by aiming at the roll of the vehicle body between the piston body 4 and the throttling groove 3. Piston body 4 at first can move in the length range of the section of flow equalizing in throttle groove 3 to move the throttle section in the throttle groove 3 gradually, because the degree of depth of throttle section reduces in proper order, consequently along with piston body 4 moves to the end in the piston chamber, the flow area of hydraulic oil is more and more littleer promptly, consequently further played the effect of avoiding the automobile body to take place to heels through piston body 4 and the cooperation of throttle groove 3.

As shown in fig. 4, a damper outer cylinder 6 is sleeved outside the piston cylinder 2 to form a hydraulic damper, the piston cylinder 2 is used as an inner cylinder of the hydraulic damper, an upper port of the damper outer cylinder 6 is hermetically arranged with the piston cylinder 2, an outer oil cavity of the hydraulic damper is formed between the damper outer cylinder 6 and the piston cylinder 2 at intervals, the piston cavity in the piston cylinder 2 becomes an inner oil cavity of the hydraulic damper, and a conventional through hole or valve body is arranged at the bottom of the piston cylinder 2 to realize communication between the inner oil cavity and the outer oil cavity.

When the vehicle body is damped, the damping can be realized by using the hydraulic damping piston without the combined sleeve or the hydraulic damper with the combined sleeve.

Example 2:

this example differs from example 1 in that: as shown in fig. 5, in the present embodiment, the cross section of the direction-changing adjusting groove 5 is triangular, and the groove wall is a straight line which is sequentially raised from the center to both sides.

Example 3:

this example differs from example 1 in that: as shown in fig. 6, in the present embodiment, a circular arc-shaped protrusion which is upwardly arched is formed at a position where the direction-changing adjustment groove 5 is opened in embodiment 1 without providing the direction-changing adjustment groove 5, a lower edge of the protrusion is a thinnest portion of the piston body 4, a center of the protrusion is a thickest portion of the piston body 4, and a position where the thinnest portion of the piston body 4 is opposed to the throttle groove 3 is defined as a start position of the piston body 4. After the piston body 4 and the piston cylinder 2 rotate relatively, the thinnest positions on the two sides of the piston body 4 are gradually staggered with the throttling grooves 3, so that the circulation length of hydraulic oil is prolonged, and the protrusions can be arranged on the lower portion of the piston body 4 independently or simultaneously.

Example 4:

this example differs from example 1 in that: as shown in fig. 7, in the present embodiment, the longitudinal section of the piston body 4 is a right trapezoid, the thickness of the piston body 4 becomes thicker in the radial direction, only one set of the throttle grooves 3 is provided in the present embodiment, and the position where the throttle grooves 3 correspond to the thinnest point of the piston body 4 is taken as the starting position of the piston body 4. After the piston body 4 and the piston cylinder 2 rotate relatively, the thickness of the piston body 4 becomes thicker gradually, so that the circulation length of the hydraulic oil is prolonged.

Example 5:

this example differs from example 1 in that: in this embodiment, the throttling section of the throttling groove 3 is designed to be multi-section instead of a slope-shaped groove with successively decreasing depth, the throttling section is divided into multiple sections from the inner side to the outer side, and the depth of each section is successively decreased.

Example 6:

this example differs from example 1 in that: in the embodiment, the direction-changing adjusting groove 5 is formed in the lower portion of the piston body 4.

While the invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention. However, any simple modification, equivalent change and modification made to the above embodiments according to the technical substance of the present invention still belong to the protection scope of the technical solution of the present invention.

Claims

1. The utility model provides a compromise hydraulic damping piston that car heeled and vibrations, is provided with piston body (4) including piston cylinder (2) that are full of hydraulic oil in piston cylinder (2), and piston body (4) are connected to piston rod (1) one end, and the other end is drawn forth from piston cylinder (2) port, and piston rod (1) drive piston body (4) at piston cylinder (2) axial reciprocating motion or/and with piston cylinder (2) circumference reciprocating rotation, its characterized in that: the inner wall of the piston cylinder (2) is provided with a throttling groove (3), the outer wall of the piston body (4) is attached to the throttling groove (3) and forms a circulation channel of hydraulic oil at intervals at the attachment surface, and when the piston body (4) axially reciprocates in the piston cylinder (2), the area of the circulation channel is reduced along with the increase of the movement amplitude of the piston body (4) from the middle part of the throttling groove (3) to two sides in the piston cylinder (2);

when the piston body (4) rotates in a reciprocating manner in the circumferential direction in the piston cylinder (2), the joint position of the throttling groove (3) and the outer wall of the piston body (4) changes in a reciprocating manner between the thinnest position and the thickest position of the piston body (4), so that the length of a circulation channel at the joint surface changes.

2. The hydraulic damping piston for roll and shock in an automobile of claim 1, wherein: the throttling grooves (3) are at least provided with one group along the axial direction on the inner wall of the piston cylinder (2).

3. The hydraulic damping piston for roll and vibration of automobiles according to claim 1 or 2, wherein: the throttling groove (3) comprises a flow equalizing section and a throttling section, the flow equalizing section is a groove with uniform depth, the throttling section extends from two ends of the flow equalizing section to two outer sides, and the throttling section is a slope-shaped groove with deep inside and shallow outside; the axial length of the flow equalizing section is longer than the thickness of the piston body (4).

4. The hydraulic damping piston for roll and shock in an automobile of claim 1, wherein: the piston comprises a piston body (4), and is characterized in that the upper part or/and the lower part of the piston body (4) is/are provided with a radial through diversion adjusting groove (5), the heights of the groove walls of the diversion adjusting groove (5) from the center to the two sides are sequentially increased, and along with the circumferential reciprocating rotation of the piston body (4) and a piston cylinder (2), the groove walls of the diversion adjusting groove (5) and the throttling groove (3) are in reciprocating staggering.

5. The hydraulic damping piston for roll and shock in an automobile of claim 1, wherein: arc-shaped bulges are arranged on the upper part or/and the lower part of the piston body (4), and the upper edge and the lower edge of each bulge are respectively the maximum part and the minimum part of the thickness of the piston body (4).

6. The hydraulic damping piston as recited in claim 4, wherein the piston is adapted to provide roll and vibration in a vehicle, and further comprising: the throttling section of the throttling groove (3) is in a multi-section type, the throttling section is divided into a plurality of sections from the inner side to the outer side, and the depth of each section is reduced in sequence.

7. The hydraulic damping piston as recited in claim 4, wherein the piston is adapted to provide roll and vibration in a vehicle, and further comprising: the cross section of the turning adjusting groove (5) is arc-shaped, and the groove wall of the turning adjusting groove is an arc line which is sequentially lifted from the center to two sides.

8. The hydraulic damping piston as recited in claim 4, wherein the piston is adapted to provide roll and vibration in a vehicle, and further comprising: the cross section of the turning adjusting groove (5) is triangular, and the groove wall of the turning adjusting groove is a straight line which sequentially rises from the center to two sides.

9. The hydraulic damping piston for roll and shock in an automobile of claim 1, wherein: the longitudinal section of the piston body (4) is in a right-angle trapezoid shape.

10. A hydraulic shock absorber comprising the hydraulic shock absorbing piston according to any one of claims 1 to 9, wherein the hydraulic shock absorbing piston is configured to absorb lateral roll and vibration of an automobile, and comprises: the outer side of the piston cylinder (2) is hermetically sleeved with a shock absorber outer cylinder (6), an outer oil cavity of the shock absorber is formed between the shock absorber outer cylinder (6) and the piston cylinder (2) at intervals, and the bottom of the piston cylinder (2) is communicated with the shock absorber outer cylinder (6).