CN108869672B - Double-hydraulic automatic tensioner for hybrid electric vehicle - Google Patents
Double-hydraulic automatic tensioner for hybrid electric vehicle Download PDFInfo
- Publication number
- CN108869672B CN108869672B CN201810946076.1A CN201810946076A CN108869672B CN 108869672 B CN108869672 B CN 108869672B CN 201810946076 A CN201810946076 A CN 201810946076A CN 108869672 B CN108869672 B CN 108869672B
- Authority
- CN
- China
- Prior art keywords
- piston rod
- cavity
- tensioner
- ring
- cylinder body
- Prior art date
- Legal status (The legal status 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 status listed.)
- Active
Links
- 238000007789 sealing Methods 0.000 claims abstract description 72
- 238000013016 damping Methods 0.000 claims abstract description 47
- 239000010720 hydraulic oil Substances 0.000 claims description 30
- 239000003921 oil Substances 0.000 claims description 13
- 230000009977 dual effect Effects 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 238000005299 abrasion Methods 0.000 abstract description 2
- 230000000149 penetrating effect Effects 0.000 abstract 1
- 229910000831 Steel Inorganic materials 0.000 description 8
- 239000010959 steel Substances 0.000 description 8
- 239000007858 starting material Substances 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 5
- 230000002829 reductive effect Effects 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000002238 attenuated effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000002146 bilateral effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
Classifications
-
- 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
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
- F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
- F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
The invention discloses a double-hydraulic automatic tensioner for a hybrid electric vehicle, which comprises an arc-shaped cylinder body, wherein two bilaterally symmetrical arc-shaped cavities are arranged in the cylinder body in a mirror image manner in an isolated manner, a hollow piston which is in an arc shape is arranged in each cavity in a sliding fit manner, one end of the hollow piston is connected with an arc-shaped piston rod, the other end of the hollow piston is abutted against the inner wall of a cylinder body isolating part which separates the two cavities through a spiral spring, a one-way valve is arranged in a central hole of the hollow piston, and a plurality of damping holes are arranged at the edge of the hollow piston in a penetrating manner; the outlet of the cavity is provided with a double-ring sealing device which is simultaneously in sealing fit with the inner wall of the cylinder body and has a unilateral sliding function, and the free end of the piston rod is rotationally connected with a tensioner belt wheel. The invention adopts the circular arc double hydraulic automatic tensioners to ensure the tension demands of belt tension in different driving modes, has compact structure, does not have the problem of abrasion compared with the friction type automatic tensioners, and has long service life.
Description
Technical Field
The present invention relates to a conveyor belt drive system mounted on an internal combustion engine having a reversible generator, or starter motor/generator, and more particularly to a dual hydraulic automatic tensioner for a hybrid vehicle.
Background
The automatic tensioner is used as an important component in an accessory driving system at the front end of an engine, and has the main functions of maintaining the tension stability of belt sections at the two ends of the automatic tensioner, increasing the wrap angle of accessory wheels, compensating the change of a belt caused by tension or abrasion and attenuating the swing of a tensioning arm caused by the fluctuation of the rotation speed of the engine, thereby avoiding the belt from skidding, noise and vibration, improving the transmission level of the system and ensuring the normal operation of the system. Currently existing automatic tensioners are largely divided into two types, friction and hydraulic. The friction type automatic tensioner generates damping by means of the relative sliding of the damping piece and the contacted surface, the friction type tensioner needs a larger installation space, and meanwhile, the damping piece can be worn along with working time, so that damping is attenuated, and the efficiency is lost. The hydraulic automatic tensioner generates damping through repeatedly compressing oil in the hydraulic automatic tensioner through the damping holes, energy of reciprocating motion is converted into heat energy of the oil, the damping size can be adjusted through the size and the number of the damping holes, the damping effect basically cannot be attenuated along with long service time, and the working state is stable and reliable.
In order to achieve the aim of energy conservation and emission reduction, the automatic start-stop function of an automobile engine is gradually popularized. When the automobile is in a stop state, the engine is stopped to save fuel; when the brake pedal is released, the engine will restart, and in order to achieve a rapid start of the engine, an integrated start/generator component is used in the engine accessory drive system, which requires two tensioners to tension the belt, as compared to conventional engine front end accessory drives.
In patent DE19926615A1 (published 12/14 2000) a tensioning device for traction is described, comprising two tensioning wheels, wherein the pivot axis of the tensioning arms of the two tensioning wheels coincides with the drive shaft of the drive pulley. The tensioner includes a flange housing for supporting a drive belt bearing shaft. The disadvantage of such a device comprising a drive shaft is that the bearing shaft of the drive pulley must be supported by the flange housing in two parts and that the design requires a significant increase in the overall axial length.
The hydraulic damping automatic tensioner described in the patent CN104235293 a is a hydraulic tensioner with wider current use, the structure divides the tensioner into an inner chamber and an outer chamber through a set cylinder, oil repeatedly flows in the inner chamber and the outer chamber through a gap between a plunger and the cylinder or a one-way valve in the compression and extension process of the tensioner to generate damping, and due to the adoption of the inner chamber and the outer chamber, the radial size of the automatic tensioner of the structure is larger, and when the oil flows out from the gap between the plunger and the cylinder, the eccentricity of the plunger is possibly caused due to uneven pressure, so that the service life of the tensioner is influenced.
In the above-mentioned known solution embodiments, in order to provide a sufficiently large tension and support of the belt, two independent tensioners are used, but it is difficult to arrange the two tensioners in a limited engine front space, while friction automatic tensioners are used, the damping being damped with time of use. When the working condition of the front-end accessory system is changed drastically, the reduced damping is insufficient to attenuate the system vibration of the same size, so that the system fluctuation is aggravated, and the swing angle of the tensioning arm is increased. The large tensioner arm pivot angle results in increased damping member wear, and therefore faster damping reduction, and poorer system response, resulting in a vicious circle. Meanwhile, the severe change of the swing angle of the tensioning arm can cause problems such as abnormal sound, the impact of the tensioning arm on a limiting block, premature failure of the tensioner and the like.
Disclosure of Invention
The invention aims to solve the problems that the front end of the engine of the hybrid electric vehicle is tense in space layout, two independent tensioners are difficult to install, and damping attenuation of a friction type automatic tensioner is overcome, and the invention can provide continuous tension and required damping for an accessory driving system at the front end of the engine and has long service life.
The technical scheme adopted for solving the technical problems is as follows:
a dual hydraulic automatic tensioner for a hybrid vehicle, comprising: the cylinder body is in an arc shape, two bilateral symmetry arc-shaped cavities are arranged in the cylinder body in a mirror image mode in an isolated mode, arc-shaped hollow pistons are arranged in each cavity in a sliding fit mode, one end of each hollow piston is connected with an arc-shaped piston rod extending out of each cavity, the other end of each hollow piston is abutted to the inner wall of a cylinder body isolating part for isolating the two cavities through a spiral spring, a one-way valve is arranged in a central hole of each hollow piston, and a plurality of damping holes penetrate through the edge of each hollow piston; the outlet of the cavity is provided with a double-ring sealing device which is simultaneously in sealing fit with the piston rod and the inner wall of the cylinder body and has a unilateral sliding function; the cavities at two ends of the hollow piston are filled with hydraulic oil; the free end of the piston rod extending out of the cavity is rotationally connected with a tensioner pulley.
Preferably, the one-way valve comprises a one-way valve body, a one-way valve steel ball and a spring which are arranged in the one-way valve body, wherein the arrangement direction of the one-way valve steel ball and the spring can only enable hydraulic oil to flow from a rod end to a rod-free end of the hollow piston.
Preferably, a V-shaped oil liquid channel communicated with the one-way valve is arranged in the middle of the rod end of the hollow piston.
Preferably, the double-ring sealing device comprises an outer annular sealing ring, an inner annular sealing ring and a spring connected between the outer annular sealing ring and the inner annular sealing ring, wherein an inner hole of the outer annular sealing ring is in reciprocating sealing fit with a piston rod, the outer peripheral wall is fixedly embedded in a positioning groove on the inner wall of the cylinder body, the inner hole of the inner annular sealing ring is in reciprocating sealing fit with the piston rod, the outer peripheral wall is in reciprocating sealing fit with the inner wall of the cylinder body, the double-ring sealing device not only plays a sealing role, but also can compensate for volume difference caused by piston movement.
Further, a free end of the piston rod extending out of the cavity is provided with a large end of the piston rod, and the large end of the piston rod is rotationally connected with the tensioner pulley through a bolt.
Preferably, a hollow sealing buffer block with one end in interference fit with the cavity is further arranged at the outlet of the cavity, and a central hole of the sealing buffer block is in reciprocating sealing fit with the piston rod to play a role in sealing the third layer.
Preferably, the other end of the sealing buffer block is provided with an arc surface matched with the opposite surface of the large end of the piston rod, so that the large end of the piston rod of the supporting belt wheel can be effectively prevented from being in direct collision contact with the cylinder body.
Preferably, the diameter of the damping hole is 0.8-1.2mm.
Preferably, the cylinder is fixed to the front end of the starter motor/generator by a mounting bracket.
Preferably, the damping holes are symmetrically distributed around the piston rod, and the number and the diameter of the damping holes are matched with those of actually required damping.
Compared with the prior art, the invention has the beneficial effects that: the tensioner adopts a double hydraulic structure to provide continuous tension and required damping for a front end accessory drive system comprising an integrated start/generator component, the damping is basically not attenuated along with the use time, the tension of a belt section is maintained constant, slipping and noise are avoided, the service life of the tensioner is prolonged, and meanwhile, the structure is compact and convenient to install.
Drawings
FIG. 1 is a schematic diagram of a typical hybrid front end belt drive system;
FIG. 2 is a transmission function of the device of FIG. 1 in generator mode;
FIG. 3 is a transmission function of the device of FIG. 1 in a start motor mode;
FIG. 4 is a schematic illustration of the structure of the automatic tensioning of an embodiment of the present invention;
FIG. 5 is an enlarged view of a check valve and a damping orifice according to an embodiment of the present invention;
FIG. 6 is a schematic diagram of the operation of the check valve of the present invention when closed;
FIG. 7 is a schematic diagram of the operation of the check valve according to the embodiment of the present invention when opened;
FIG. 8 is an enlarged partial view of a first double ring seal of an embodiment of the present invention;
FIG. 9 is a graph of piston rod speed versus orifice diameter and number for an embodiment of the present invention.
The drawings are marked with the following description: 0-front end accessory drive system, 1-crankshaft pulley, 2-belt, 3-driven idler pulley, 4-air conditioner compressor, 5-water pump, 6-starter motor/generator pulley, 7-first tensioner pulley, 8-second tensioner pulley, 9-mounting bracket, 10-first bolt, 11-second bolt, 12-first piston rod big end, 13-second piston rod big end, 14-first seal buffer block, 15-second seal buffer block, 16-first double ring seal device, 17-second double ring seal device, 16 a-outside ring seal, 16B-inside ring seal, 16 c-spring, 18-first piston rod, 19-second piston rod, 20-first piston rod cavity, 21-second piston rod cavity, 22-first oil channel, 23-second oil channel, 24-first hollow piston, 25-second hollow piston, 26-first damping hole, 27-second damping hole, 28-first check valve, 28 a-first check valve steel ball, 28B-first spring, 28 c-first check valve body, 29-second check valve, 29 a-second check valve steel ball, 29B-second spring, 29 c-second check valve body, 30-first coil spring, 31-second coil spring, 32-first coil spring cavity, 33-second coil spring cavity, 34-hydraulic oil, 35-cylinder, A-first tensioner, B-second tensioner.
Detailed Description
For a better understanding of the present invention, embodiments of the present invention are described in further detail below with reference to the drawings.
Fig. 1 shows a typical Front End Accessory Drive (FEAD) system 0 using a belt 2 to connect a crankshaft pulley 1, a driven idler pulley 3, an air conditioning compressor 4, a water pump 5, a starter motor/generator pulley 6, a first tensioner pulley 7 and a second tensioner pulley 8.
Fig. 2 is a generator mode. When operating in generator mode, the first tensioner pulley 7 is forced by belt tight tension to the seal cushion position or some equilibrium position to become a fixed idler, and the second tensioner B will operate as an automatic tensioner.
Fig. 3 is a start motor mode: when operating in the starter motor mode, the second tensioner pulley 8 is forced by the belt tight tension to the seal cushion position or some equilibrium position to become a fixed idler, and the first tensioner a will operate as an automatic tensioner.
As shown in fig. 4, a dual hydraulic automatic tensioner for a hybrid vehicle includes a circular arc-shaped cylinder 35, a first coil spring 30, a second coil spring 31, hydraulic oil 34, a first hollow piston 24, a second hollow piston 25, a first double ring sealing device 16, a second double ring sealing device 17, a first sealing buffer block 14, a second sealing buffer block 15, a first tensioner pulley 7, a second tensioner pulley 8, a mounting bracket 9 mounted at the front end of a starter motor/generator, a cylinder 35 fixed on the mounting bracket 9, the cylinder 35 having a circular arc shape, the cylinder 35 being divided into two at the middle, a first tensioner a on the left, a second tensioner B on the right, one ends of the first piston rod 18 and the second piston rod 19 extending out of the cylinder 35, the ends thereof being respectively an elliptical-like first piston rod large end 12, a second piston rod large end 13, the first tensioner pulley 7 and the second tensioner pulley 8 are respectively fixed on the first piston rod big end 12 and the second piston rod big end 13 through a first bolt 10 and a second bolt 11, the other ends of the first piston rod 18 and the second piston rod 19 sequentially pass through a first sealing buffer block 14, a second sealing buffer block 15, a first double-ring sealing device 16 and a second double-ring sealing device 17 along the arc-shaped cavity of an arc-shaped cylinder body 35 and then are connected with a first hollow piston 24 and a second hollow piston 25, the left cavity and the right cavity of the first hollow piston 24 and the second hollow piston 25 are divided into a first spiral spring cavity 32, a second spiral spring cavity 33, a first piston rod cavity 20 and a second piston rod cavity 21, a first check valve 28 and a second check valve 29 with the same structure are arranged on the central holes of the first hollow piston 24 and the second hollow piston 25, the rod ends of the first hollow piston 24 and the second hollow piston 25 are respectively provided with a V-shaped first oil liquid channel 22 and a V-shaped second oil liquid channel 23 which are communicated with corresponding one-way valves in the middle. The first check valve 28 mainly comprises a first check valve steel ball 28a, a first spring 28b and a first check valve body 28c, the second check valve 29 mainly comprises a second check valve steel ball 29a, a second spring 29b and a second check valve body 29c, and meanwhile, the first hollow piston 24 and the second hollow piston 25 are respectively provided with a plurality of first damping holes 26 and second damping holes 27 symmetrically arranged around the piston rod for generating damping, as shown in fig. 5. When the spiral springs are stretched, the hydraulic oil 34 can enter the piston rod cavity from the spiral spring cavity through the one-way valve and the oil liquid channel, and the first spiral spring 30 and the second spiral spring 31 are respectively installed between the first hollow piston 24, the second hollow piston 25 and the inner wall of the isolation part of the cylinder body 35 in a pressed mode.
As shown in fig. 8, which is an enlarged view of the first double-ring sealing device 16, the first double-ring sealing device 16 includes an outer annular sealing ring 16a, an inner annular sealing ring 16b, and a spring 16c connected between the outer annular sealing ring 16a and the inner annular sealing ring 16b, wherein an inner hole of the outer annular sealing ring 16a is in reciprocating sealing engagement with the first piston rod 18, a peripheral wall is fixedly embedded in a positioning groove on an inner wall of the cylinder 35 to limit the movement of the outer annular sealing ring 16a, an inner hole of the inner annular sealing ring 16b is in reciprocating sealing engagement with the first piston rod 18, and a peripheral wall is in reciprocating sealing engagement with the inner wall of the cylinder 35, the inner annular sealing ring 16b can slide along the inner wall of the cylinder 35 when being stressed, and the outer annular sealing ring 16a and the inner annular sealing ring 16b are connected by the spring 16c, the structure is designed to compensate for insufficient volume of hydraulic oil in the first piston rod 20 due to the existence of the first piston rod 18 when the first spiral spring chamber 32 enters the first piston rod chamber 20, to accommodate hydraulic oil entering the first spiral spring chamber 32, and to work as a double-ring sealing device of the first piston rod 16 is an example: when the hydraulic oil 34 in the first coil spring chamber 32 enters the first piston rod chamber 20, the volume of the first piston rod chamber 20 is insufficient to accommodate the hydraulic oil 34 in the first coil spring chamber 32 entering the first piston rod chamber 20 due to the existence of the first piston rod 18, the inner annular sealing ring 16b is pressed by the hydraulic oil pressure in the first piston rod chamber 20, so that the inner annular sealing ring 16b rotates anticlockwise around the circle center of the circular arc cylinder 35 along the inner cavity of the cylinder 35, the volume of the first piston rod chamber 20 is increased to accommodate the hydraulic oil 34 in the first piston rod chamber 20 from the first coil spring chamber 32, and when the hydraulic oil 34 enters the first coil spring chamber 32 from the first piston chamber 20, the pressure in the first piston rod chamber 20 is reduced, and the inner annular sealing ring 16b rotates clockwise around the circle center of the circular arc cylinder 35 along the inner cavity of the cylinder 35 under the action of the spring 16c, so that an equilibrium position is achieved again. The second double ring seal 17 is similar in structure and function to the first double ring seal 16 and will not be described in detail herein.
As shown in fig. 8, the first sealing buffer block 14 is of a hollow structure, one end of the first sealing buffer block is in interference fit with the outlet of the cavity of the cylinder 35, so as to play a role in sealing the third layer, and can well prevent hydraulic oil in the cylinder from overflowing, the other end of the first sealing buffer block 14 is a cambered surface, the cambered surface is the same as the opposite surface of the large end 12 of the first piston rod, so that the piston rod can be effectively prevented from supporting the pulley end to be in direct contact with the cylinder, the buffering effect is achieved, and the central hole of the first sealing buffer block 14 is in reciprocating sealing fit with the first piston rod 18. The second sealing buffer block 15 has a structure and function similar to those of the first sealing buffer block 14, and will not be described again.
As shown in fig. 9, the corresponding relationship curve of the piston rod speed v with the change of the damping hole diameter d is shown in the case of different damping hole numbers, it can be seen that the piston rod speed v increases with the increase of the damping hole diameter d, and the larger d is, the larger v is amplified, so in the actual design, d needs to be very small, and in this embodiment, 1mm is needed to obtain a good damping effect. When the diameter of the damping holes is fixed, the speed of the piston rod is reduced along with the increase of the number of the damping holes. Therefore, the damping of the double-hydraulic automatic tensioner can be adjusted according to actual needs to the number and the diameter of the damping holes so as to adapt to different working conditions.
The specific working process of the double-hydraulic automatic tensioner provided by the embodiment is as follows:
when in the generator mode, the first tensioner pulley 7 is extruded by the belt 2, the first piston rod 18 pushes the first hollow piston 24 to rotate clockwise along the circular arc-shaped cavity, so that the first spiral spring 30 is compressed, the pressure of the first spiral spring cavity 32 is increased, hydraulic oil 34 acts on the first one-way valve 28, the first one-way valve 28 is closed, hydraulic oil 34 of the first spiral spring cavity 32 can only enter the first piston rod cavity 20 through the first damping hole 26, as shown in fig. 6, arrows show the flow direction of the hydraulic oil, damping is generated when the hydraulic oil passes through the first damping hole 26, the movement speed of the first piston rod 18 is slowed down, the movement of the first piston rod 18 is converted into the heat energy of the hydraulic oil, vibration of the tensioner is damped, vibration caused by the belt is consumed, the side of the second tensioner B is changed from the tight side to the loose side, the belt tension acting on the second tensioner pulley 8 is reduced, the second spiral spring 31 stretches, the second tensioner pulley 19 rotates clockwise rapidly along the circular arc-shaped cavity under the action of the second spiral spring 31, and the second tensioner pulley 8 can be prevented from providing slipping. At this time, the pressure of the hydraulic oil 34 in the second coil spring chamber 33 is smaller than the pressure of the hydraulic oil in the second piston rod chamber 21, that is, the pressure of the hydraulic oil in the second piston rod chamber 21 acting on the second check valve steel ball 29a is larger than the pressure of the hydraulic oil in the second spring 29b and the second coil spring chamber 33 acting on the second check valve steel ball 29a, so that the second spring 29b is compressed, the second check valve 29 is opened, and the hydraulic oil 34 flows back to the second coil spring chamber 33 through the second oil channel 23 and the second check valve 29, as shown in fig. 7, and the arrows indicate the flow direction of the hydraulic oil. When the motor is started, the side of the first tensioner A is changed from the tight side to the loose side, the tension acting on the first tensioner pulley 7 is reduced, the first piston rod 18 rapidly stretches out in the anticlockwise direction under the action of the first spiral spring 30, the first tensioner pulley 7 is tightly attached to the belt, the belt slip is avoided, the pressure of hydraulic oil 34 in the first spiral spring cavity 32 is smaller than the pressure of the first piston rod cavity 20, the first one-way valve 28 is opened, hydraulic oil 34 enters the first spiral spring cavity 32 from the first piston rod cavity 20 through the first oil channel 22 and the first one-way valve 28, the side of the second tensioner B is changed from the loose side to the tight side, the tension acting on the second tensioner pulley 8 is increased, the second piston rod 19 moves in the anticlockwise direction, the second piston 25 compresses the second spiral spring 31, the pressure of hydraulic oil 34 in the second spiral spring cavity 33 is larger than the pressure of the second piston rod cavity 21, the second one-way valve 29 is closed, the hydraulic oil 34 in the second spiral spring cavity 33 can only enter the second cavity 21 through the second hole 27, and vibration damping heat energy is damped by the vibration of the second piston rod 27, vibration is damped, and vibration is generated by vibration of the vibration is damped.
The above-described embodiment is only a preferred embodiment of the present invention, and is not limited in any way, and other variations and modifications may be made without departing from the technical aspects set forth in the claims.
Claims (8)
1. A dual hydraulic automatic tensioner for a hybrid vehicle, comprising: the cylinder body (35) is fixed at the front end of the starting motor/generator through a mounting bracket (9), two bilaterally symmetrical circular arc-shaped cavities are arranged in the cylinder body (35) in a mirror image mode in a mutually isolated mode, circular arc-shaped hollow pistons are arranged in each cavity in a sliding fit mode, one end of each hollow piston is connected with an arc-shaped piston rod extending out of each cavity, the other end of each hollow piston is abutted to the inner wall of a separating part of the cylinder body (35) for separating the two cavities through a spiral spring, a one-way valve is arranged in a central hole of each hollow piston, a plurality of damping holes penetrate through the edge of each hollow piston, the damping holes are symmetrically distributed around the piston rod, and the number and the diameter of each damping hole are matched with those of actually required damping; the outlet of the cavity is provided with a double-ring sealing device which is simultaneously in sealing fit with the piston rod and the inner wall of the cylinder body (35) and has a unilateral sliding function; the cavities at two ends of the hollow piston are filled with hydraulic oil (34); the free end of the piston rod extending out of the cavity is rotationally connected with a tensioner pulley.
2. The dual hydraulic automatic tensioner of claim 1, wherein the check valve comprises a check valve body, a check valve ball disposed within the check valve body, and a spring disposed in a direction that allows hydraulic oil to flow only from the rod end to the rod end of the hollow piston.
3. A dual hydraulic automatic tensioner according to claim 1 or 2, characterized in that the hollow piston has a V-shaped oil passage centrally provided in the end of the rod communicating with the one-way valve.
4. The dual hydraulic automatic tensioner of claim 1, wherein the double-ring sealing device comprises an outer ring-shaped sealing ring, an inner ring-shaped sealing ring and a spring connected between the outer ring-shaped sealing ring and the inner ring-shaped sealing ring, an inner hole of the outer ring-shaped sealing ring is in reciprocating sealing fit with a piston rod, an outer peripheral wall is fixedly embedded in a positioning groove on the inner wall of the cylinder body (35), the inner hole of the inner ring-shaped sealing ring is in reciprocating sealing fit with the piston rod, and the outer peripheral wall is in reciprocating sealing fit with the inner wall of the cylinder body (35).
5. The dual hydraulic automatic tensioner of claim 1, wherein the free end of the piston rod extending out of the cavity is provided with a piston rod large end, the piston rod large end being rotatably connected to the tensioner pulley by a bolt.
6. The dual hydraulic automatic tensioner of claim 5, wherein a hollow sealing buffer block having one end in interference fit with the cavity is further provided at the outlet of the cavity, and a central hole of the sealing buffer block is in reciprocating sealing fit with the piston rod.
7. The dual hydraulic automatic tensioner of claim 6, wherein the other end of the sealing cushion block is provided with a cambered surface that mates with an opposite surface of the piston rod large end.
8. The dual hydraulic automatic tensioner of claim 1, wherein the orifice diameter is 0.8-1.2mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810946076.1A CN108869672B (en) | 2018-08-20 | 2018-08-20 | Double-hydraulic automatic tensioner for hybrid electric vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810946076.1A CN108869672B (en) | 2018-08-20 | 2018-08-20 | Double-hydraulic automatic tensioner for hybrid electric vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108869672A CN108869672A (en) | 2018-11-23 |
| CN108869672B true CN108869672B (en) | 2023-12-01 |
Family
ID=64319188
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810946076.1A Active CN108869672B (en) | 2018-08-20 | 2018-08-20 | Double-hydraulic automatic tensioner for hybrid electric vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108869672B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109695677B (en) * | 2019-03-07 | 2023-12-05 | 河北工业大学 | Automatic tensioner with gas-liquid reinforcement cylinder |
| CN111734802A (en) * | 2019-03-25 | 2020-10-02 | 舍弗勒技术股份两合公司 | Belt tensioner |
| CN110375043A (en) * | 2019-06-25 | 2019-10-25 | 宁波丰茂远东橡胶有限公司 | Automatic tensioner with viscous damping property |
| CN113969962B (en) * | 2020-07-22 | 2023-11-21 | 广州汽车集团股份有限公司 | Tensioner and automobile engine transmission system with same |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010093081A1 (en) * | 2009-02-10 | 2010-08-19 | 지엠비코리아 주식회사 | Hydraulic auto tensioner for vehicle belt drive |
| CN104995430A (en) * | 2013-02-22 | 2015-10-21 | 舍弗勒技术股份两合公司 | Starter generator belt tensioner |
| CN105864378A (en) * | 2016-04-07 | 2016-08-17 | 宁波丰茂远东橡胶有限公司 | Belt tensioning equipment of hybrid electric vehicle |
| CN107387692A (en) * | 2017-08-25 | 2017-11-24 | 华南理工大学 | A kind of motor head accessory of hydraulic formula automatic tensioner |
| CN207246346U (en) * | 2017-09-06 | 2018-04-17 | 宁波丰茂远东橡胶有限公司 | A kind of two-way tensioning apparatus of double damping structures |
| CN208858877U (en) * | 2018-08-20 | 2019-05-14 | 华南理工大学 | A kind of Double-hydraulic automatic tensioner for hybrid vehicle |
-
2018
- 2018-08-20 CN CN201810946076.1A patent/CN108869672B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010093081A1 (en) * | 2009-02-10 | 2010-08-19 | 지엠비코리아 주식회사 | Hydraulic auto tensioner for vehicle belt drive |
| CN104995430A (en) * | 2013-02-22 | 2015-10-21 | 舍弗勒技术股份两合公司 | Starter generator belt tensioner |
| CN105864378A (en) * | 2016-04-07 | 2016-08-17 | 宁波丰茂远东橡胶有限公司 | Belt tensioning equipment of hybrid electric vehicle |
| CN107387692A (en) * | 2017-08-25 | 2017-11-24 | 华南理工大学 | A kind of motor head accessory of hydraulic formula automatic tensioner |
| CN207246346U (en) * | 2017-09-06 | 2018-04-17 | 宁波丰茂远东橡胶有限公司 | A kind of two-way tensioning apparatus of double damping structures |
| CN208858877U (en) * | 2018-08-20 | 2019-05-14 | 华南理工大学 | A kind of Double-hydraulic automatic tensioner for hybrid vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108869672A (en) | 2018-11-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108869672B (en) | Double-hydraulic automatic tensioner for hybrid electric vehicle | |
| CN100430625C (en) | A two-arm belt tensioner for a belt drive | |
| US6557438B2 (en) | Breather structure of internal combustion engine for vehicles | |
| US20070142145A1 (en) | Automotive accessory drive system | |
| CN107076278B (en) | Endless drive and improved two-arm tensioning system for an endless drive | |
| EP1334290B1 (en) | Accessory drive system including a motor/generator | |
| JP2008501912A (en) | Traction mechanism | |
| US20060276284A1 (en) | Automotive accessory drive system and method of operation | |
| JP6491238B2 (en) | Torsional vibration damper with interlocked isolator | |
| US10578011B2 (en) | Motive-power transmission device for supercharger | |
| KR20070113013A (en) | An air compressor | |
| KR101300337B1 (en) | Guiding unit for a traction mechanism drive | |
| US20050148420A1 (en) | Autotensioner | |
| KR960013936B1 (en) | Fan clutch | |
| CN106931111B (en) | Double-swing-arm type automatic tensioner | |
| EP2381131B1 (en) | Hydraulic auto-tensioner and belt transmission device | |
| JP2018040399A (en) | Hydraulic automatic tensioner | |
| JP2006312969A (en) | Hydraulic automatic tensioner | |
| TWI267599B (en) | Driven pulley device of V-belt type automatic transmission | |
| CN109695677B (en) | Automatic tensioner with gas-liquid reinforcement cylinder | |
| CN208858877U (en) | A kind of Double-hydraulic automatic tensioner for hybrid vehicle | |
| CN209943443U (en) | Automatic tensioner with gas-liquid boosting cylinder | |
| CN111486203B (en) | Belt tensioning mechanism | |
| JP4494235B2 (en) | Clutch lubrication equipment | |
| CN218953433U (en) | Engine front end train with decoupling pulley |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |