CN115742648A - Two-stage transmission low-height independent suspension system and application - Google Patents
Two-stage transmission low-height independent suspension system and application Download PDFInfo
- Publication number
- CN115742648A CN115742648A CN202211459764.8A CN202211459764A CN115742648A CN 115742648 A CN115742648 A CN 115742648A CN 202211459764 A CN202211459764 A CN 202211459764A CN 115742648 A CN115742648 A CN 115742648A
- Authority
- CN
- China
- Prior art keywords
- cross arm
- frame
- hinged
- hydro
- suspension system
- 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.)
- Pending
Links
Images
Landscapes
- Vehicle Body Suspensions (AREA)
Abstract
The invention belongs to the technical field of suspension systems, and discloses a two-stage transmission low-height independent suspension system and application thereof, wherein the system comprises: the device comprises wheels, a steering knuckle, a frame, an upper cross arm, a lower cross arm, a rocker arm and a hydro-pneumatic spring; the wheels are connected with a steering knuckle through a bearing, and the upper cross arm and the lower cross arm are positioned between the steering knuckle and the frame; two ends of the upper cross arm are respectively hinged with a steering knuckle and a frame, and two ends of the lower cross arm are respectively hinged with the steering knuckle and the frame; the rocker arm is hinged to the frame and comprises an input end and an output end, a push rod is hinged to the lower cross arm, one end, far away from the lower cross arm, of the push rod is hinged to the input end, and two ends of the hydro-pneumatic spring are hinged to the frame and the output end respectively. The overall height and the gravity center height of the chassis can be reduced, and the problem that the operation stability and the driving smoothness of the chassis are influenced by the increase of the unsprung mass of the electric wheel is solved.
Description
Technical Field
The invention relates to a suspension system suitable for a heavy chassis, in particular to a two-stage transmission low-height independent suspension system and application thereof.
Background
The description of the background of the invention pertaining to the related art to which the present invention pertains is given for the sole purpose of illustrating and facilitating an understanding of the summary of the invention and is not to be construed as an admission that the applicant is explicitly aware or inferred as prior art to the filing date of the first filed application for the present invention.
The reduction of the height of the chassis is beneficial to increasing the loading space of the vehicle, the reduction of the height of the mass center of the whole vehicle and the improvement of the driving safety, and the development of the low-height suspension technology is an important direction for the development of the vehicle. The hydro-pneumatic spring and the like are used as vibration damping elements, when the hydro-pneumatic spring is applied to a chassis suspension system, a vertical mounting mode is generally adopted, the suspension system transfers load from wheels to a frame along the vertical direction, and a load transfer path is simple and direct. However, when the requirement on the passing ability of the chassis is high and the wheel jumping stroke is large, the hydro-pneumatic spring is long, and the height of the hydro-pneumatic spring is too high, so that the loading space of the upper load is influenced, and the loading height has to be increased.
With the application of the vehicle electric driving technology in the field of automobile chassis, the highly integrated electric wheel technology is gradually oriented to practicality. The electric wheel technology is applied to automobiles to reduce power transmission chains and improve the efficiency and the space utilization rate of the chassis. Meanwhile, the electric wheel does not need a transmission shaft to input power, and the middle part of the frame is added with a design space.
Disclosure of Invention
The embodiment of the invention aims to provide a two-stage transmission low-height independent suspension system and application thereof, which can reduce the overall height and the gravity center height of a chassis and solve the problem that the control stability and the driving smoothness of the chassis are influenced by the increase of unsprung mass of an electric wheel.
The purpose of the embodiment of the invention is realized by the following technical scheme:
a two-stage transmission low-height independent suspension system comprises wheels, a steering knuckle, a frame, an upper cross arm, a lower cross arm, a rocker arm and a hydro-pneumatic spring; the wheels are connected with a steering knuckle through a bearing, and the upper cross arm and the lower cross arm are positioned between the steering knuckle and the frame; two ends of the upper cross arm are respectively hinged with a steering knuckle and a frame, and two ends of the lower cross arm are respectively hinged with the steering knuckle and the frame; the rocker arm is hinged to the frame and comprises an input end and an output end, a push rod is hinged to the lower cross arm, one end, far away from the lower cross arm, of the push rod is hinged to the input end, and two ends of the hydro-pneumatic spring are hinged to the frame and the output end respectively.
Furthermore, the upper cross arm is hinged with the steering knuckle by a ball pin; the lower cross arm is hinged with the steering knuckle by a ball pin.
Furthermore, the push rod is hinged to the middle of the lower cross arm.
Furthermore, the rocker arm is triangular, and three corners of the rocker arm are respectively hinged with the push rod, the hydro-pneumatic spring and the frame.
Furthermore, a rocker arm bracket is fixed on the frame, and the rocker arm is hinged with the rocker arm bracket.
Furthermore, a cushion is arranged at the bottom of the frame.
Furthermore, the frame is provided with a hydro-pneumatic spring support, and the hydro-pneumatic spring is hinged with the hydro-pneumatic spring support.
Furthermore, an oil source interface is arranged on the oil-gas spring.
Furthermore, a stopper is arranged on the upper cross arm and is positioned between the steering knuckle and the hydro-pneumatic spring.
The application of the two-stage transmission low-height independent suspension system is used for reducing the height of a heavy chassis and the gravity center of a whole vehicle.
The embodiment of the invention has the following beneficial effects:
the low-height suspension frame transmits the load on the cross arm to the transverse hydro-pneumatic spring through the rocker arm, can effectively reduce the height of the whole vehicle and the height of the gravity center, has the functions of adjusting the height of a chassis and quickly exhibiting the vehicle to land, realizes quick vehicle exhibition, and simultaneously improves the control performance of a running system by utilizing the two-stage transmission ratio of the suspension frame.
According to the low-height suspension, the oil-gas spring is transversely arranged, the occupied space is small, the height of the heavy chassis and the gravity center of the whole vehicle are reduced, the vehicle can pass through a bend at a higher speed, the rolling amplitude is small during the bending, the operation stability and the driving smoothness of a suspension system are improved, and the functions of height adjustment of the heavy chassis and vehicle floor unfolding during the static state are realized.
Drawings
FIG. 1 is a schematic structural diagram of a conventional heavy chassis double wishbone suspension;
FIG. 2 is a layout diagram of a two-stage transmission low-height independent suspension system;
FIG. 3 is a block diagram of a two-stage drive low-height independent suspension system;
FIG. 4 is a schematic diagram of a height adjustment actuator of a two-stage transmission low-height independent suspension system;
fig. 5 is a schematic view of the heavy chassis landing.
Detailed Description
The present application is further described below with reference to examples.
In the following description, different "one embodiment" or "an embodiment" may not necessarily refer to the same embodiment, in order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art. Various embodiments may be replaced or combined, and other embodiments may be obtained according to the embodiments without creative efforts for those skilled in the art.
Referring to fig. 1, the conventional heavy chassis double wishbone suspension comprises wheels 101, a knuckle 102, an upper ball pin 103, an upper cross arm 104, a frame 105, a lower ball pin 106, a lower wishbone 107, a hydro-pneumatic spring 108, and an upper lug 109;
the wheel 101 is connected with a steering knuckle 102 through a bearing, the upper end of the steering knuckle 102 is connected with one end of an upper cross arm 104 through an upper ball pin 103, and the other end of the upper cross arm 104 is hinged with a frame 105;
the lower end of the steering knuckle 102 is connected with one end of a lower cross arm 107 through a lower ball pin 106, the other end of the lower cross arm 107 is hinged with the frame 105, the middle part of the lower cross arm 107 is hinged with the lower end of a hydro-pneumatic spring 108, the upper end of the hydro-pneumatic spring 108 is hinged with an upper lug 109, the upper lug 109 is fixed with the frame,
the conventional frame 105 of the heavy chassis double-wishbone suspension transfers ground impact load on wheels 101 to an upper wishbone 104 and a lower wishbone 107 through an upper ball pin 103 and a lower ball pin 106 on a steering knuckle 102, the upper wishbone 104 and the lower wishbone 107 transfer vertical load to a hydro-pneumatic spring 108, an oil circuit interface of the hydro-pneumatic spring 108 is connected to an energy accumulator, an oil source and a height-adjusting control system through high-pressure pipelines, high-pressure oil and gas provided by the oil source and the energy accumulator are used for relieving impact and absorbing impact load of the ground on a running system, and the load of the hydro-pneumatic spring 108 is transferred to the frame 105 through an upper lug 109.
Referring to fig. 2-5, a two-stage transmission low-height independent suspension system comprises wheels 201, a steering knuckle 202, a frame 204, an upper cross arm 203, a lower cross arm 207, a rocker arm 206 and a hydro-pneumatic spring 205; the wheels 201 are connected with a steering knuckle 202 through bearings, and the upper cross arm 203 and the lower cross arm 207 are positioned between the steering knuckle 202 and a frame 204; two ends of the upper cross arm 203 are respectively hinged with the steering knuckle 202 and the frame 204, and two ends of the lower cross arm 207 are respectively hinged with the steering knuckle 202 and the frame 204 (connected with the frame through a pin shaft 216); the rocker arm 206 is hinged on the frame 204, the rocker arm 206 comprises an input end and an output end, a push rod 217 is hinged on the lower cross arm 207, one end of the push rod 217, which is far away from the lower cross arm 207, is hinged with the input end, and two ends of the hydro-pneumatic spring 205 are respectively hinged with the frame 204 and the output end.
In some embodiments of the present invention, the upper cross arm 203 is hinged with the knuckle 202 by a ball pin; in some embodiments, upper cross arm 203 is articulated with knuckle 202 by upper ball pin 211; the lower cross arm 207 is hinged to the steering knuckle 202 by a ball pin, and in some embodiments, the lower cross arm 207 is hinged to the steering knuckle 202 by a lower ball pin 210. It is understood that the ball pin hinge is generally a ball type hinge with one hinge end and a ball pin cover matching with the other hinge end, which will not be described herein.
In some embodiments of the present invention, the push rod 217 is hinged to the middle of the lower cross arm 207. It will be appreciated that the articulation may generally be accomplished by a pin 209 as shown to pin one end of the push rod 217 to the middle of the lower cross arm 207.
In some embodiments of the present invention, the swing arm 206 has a triangular shape, and three corners of the swing arm 206 are respectively hinged to the push rod 217, the hydro-pneumatic spring 205 and the frame 204. As shown, the pins 208 may be used in all three corners.
In some embodiments of the present invention, a rocker arm bracket 213 is fixed to the frame 204, and the rocker arm 206 is hinged to the rocker arm bracket 213. The position and shape of the rocker arm stand 213 are not limited.
In some embodiments of the present invention, the bottom of the frame 204 is provided with a cushion 214. The material, size, etc. of the cushion 214 are not limited as long as it can provide cushioning.
In some embodiments of the present invention, the frame 204 is provided with a hydro-pneumatic spring support 212, and the hydro-pneumatic spring 205 is hinged to the hydro-pneumatic spring support 212.
In some embodiments of the present invention, the oil spring 205 is provided with an oil source interface 218.
In some embodiments of the present invention, the upper cross arm 203 is provided with a stopper 215, and the stopper 215 is located between the knuckle 202 and the hydro-pneumatic spring 205.
The application of the two-stage transmission low-height independent suspension system is to reduce the height of a heavy chassis and the gravity center of a whole vehicle.
The invention adopts a hydro-pneumatic spring transverse arrangement and two-stage transmission ratio, wherein the low-height suspension comprises an upper cross arm, a lower cross arm, a push rod, a rocker arm, a hydro-pneumatic spring and a mounting part. On low high suspension transmitted horizontal hydro-pneumatic spring through the load of rocking arm on with the xarm, can effectively reduce whole car height and focus height, possess chassis height adjustable and quick exhibition car function of falling to the ground, realize quick exhibition car, utilize suspension secondary drive ratio to promote the system of traveling to control the performance simultaneously.
According to the low-height suspension, the oil-gas spring is transversely arranged, the occupied space is small, the height of the heavy chassis and the gravity center of the whole vehicle are reduced, the vehicle can pass through a curve at a higher speed, the rolling amplitude is small during the passing through of the curve, the control stability and the driving smoothness of a suspension system are improved, and the landing function of the vehicle can be realized during the height adjustment and the standing of the heavy chassis.
The overall height and the gravity center height of the heavy chassis are effectively reduced by the transverse hydro-pneumatic spring;
the two-stage transmission ratio design solves the problems of operation stability and smoothness caused by the increase of unsprung mass;
heavy chassis altitude mixture control can improve trafficability characteristic and realize that quick exhibition car falls to the ground.
Aiming at the problems of the application of a double-cross-arm suspension on a heavy chassis, a two-stage transmission low-height independent suspension system is designed, an electric wheel steering knuckle is respectively connected with an upper cross arm and a lower cross arm through an upper ball pin assembly and a lower ball pin assembly, the upper cross arm is connected with a cross-arm support on a frame through a pin shaft and swings up and down around the pin shaft; the inner end of the lower cross arm is connected with a cross arm support on the frame by a pin shaft and swings up and down around the pin shaft; and a push rod hinged at the middle part of the lower cross arm is connected with the rocker arm, so that the vertical load of the suspension is transmitted to the input end of the rocker arm through the push rod, and the rocker arm is driven to rotate around the pin shaft. The rocker pin shaft is installed on a rocker support of the frame, an input end and an output end are designed on the rocker, the input end load and the motion are transferred to the output end through the rotation of the rocker, the output end of the rocker is connected to a piston rod of an oil-gas spring, and the oil-gas spring plays the roles of buffering impact and absorbing vibration.
The oil-gas spring is transversely arranged in the two-stage transmission low-height independent suspension system, so that the phenomenon that the chassis is overhigh due to the fact that the oil-gas spring is vertically arranged is avoided, and therefore the height of a vehicle body and the height of the center of gravity can be greatly reduced. The gravity center of the whole vehicle is lowered, the over-bending speed of the vehicle is improved, and the roll amplitude of the vehicle during rapid over-bending is reduced. The suspension provides excellent lateral support to the vehicle, thereby allowing the vehicle to achieve higher handling limits in curves. Meanwhile, the transverse hydro-pneumatic spring can reduce the unsprung mass of the vehicle, the vehicle can react more swiftly to obtain excellent control, and the lighter unsprung mass can be replaced by more comfortable riding experience.
With reference to fig. 3, under the condition of meeting the requirements of the bearing capacity of an automobile chassis and the large-stroke motion of a suspension, the two-stage transmission low-height independent suspension system arranges a combined part (oil-gas spring) of an elastic element and a damping element at the inner side of a frame, fills the vacant position in the middle of the rear part of the automobile due to the adoption of a hub motor, and is suitable for the structural characteristics of the whole automobile. The low-height suspension adopts an upper cross arm and a lower cross arm to control the movement of wheels, but a hydro-pneumatic spring connected with the lower cross arm is replaced by a push rod, and the hydro-pneumatic spring is completely hidden in the vehicle body. The hydro-pneumatic springs are not required to be vertically arranged, so that the height of the vehicle body can be greatly reduced, two hydro-pneumatic springs of two wheels can share one mounting support, the space can be saved, and the weight can be reduced. Meanwhile, the horizontal bearing force of the left hydro-pneumatic spring and the right hydro-pneumatic spring can be offset, and the load of the frame longitudinal beam is reduced.
Referring to fig. 4, the suspension height adjusting actuator mainly includes a hydro-pneumatic spring, an accumulator, a control valve set, an oil pump, an oil tank, a hydraulic oil circuit, and the like. The control valve group comprises 3 valve groups. The valve group 1 and the valve group 2 are respectively a heightening point control valve block for respectively controlling heightening of the left oil-gas suspension group and the right oil-gas suspension group, the valve group 3 is an oil source control valve block for ensuring pressure and flow when the heightening system normally works, when the chassis is lifted, high-pressure oil of a chassis hydraulic system enters the oil-gas suspension through the control valve block, and the oil-gas suspension extends; when the chassis is lowered, the oil gas suspension is shortened, and oil returns to the oil tank after passing through the control valve group. Meanwhile, a standby interface is designed in the oil-gas suspension serial pipeline, so that manual heightening is ensured through an external oil source when the heightening control system fails.
Referring to fig. 5, the heavy chassis is stopped on a flat ground, the suspension control switch is pressed, the suspension heightening controller sends a chassis lowering command, the chassis hydraulic system control valve group is opened, high-pressure oil returns to an oil tank from the oil-gas suspension through the control valve group, the oil-gas spring is shortened, and the wheels are greatly lifted due to the small stroke change of the oil-gas spring by depending on the two-stage transmission ratio of the suspension system; the chassis slowly descends until the bottom soft cushion contacts the ground until the chassis stops descending, at the moment, the wheels contact the ground but large supporting force is not generated, and the chassis is supported on the ground by the soft cushion to finish the floor falling process of the chassis.
It should be noted that the above embodiments can be freely combined as necessary. The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A two-stage transmission low-height independent suspension system is characterized by comprising wheels, a steering knuckle, a frame, an upper cross arm, a lower cross arm, a rocker arm and a hydro-pneumatic spring; the wheels are connected with a steering knuckle through a bearing, and the upper cross arm and the lower cross arm are positioned between the steering knuckle and the frame; two ends of the upper cross arm are respectively hinged with the steering knuckle and the frame, and two ends of the lower cross arm are respectively hinged with the steering knuckle and the frame; the rocker arm is hinged to the frame and comprises an input end and an output end, a push rod is hinged to the lower cross arm, one end, far away from the lower cross arm, of the push rod is hinged to the input end, and two ends of the hydro-pneumatic spring are hinged to the frame and the output end respectively.
2. A two-stage drive low profile independent suspension system as claimed in claim 1 wherein said upper cross arm is ball-pin articulated to the knuckle; the lower cross arm is hinged with the steering knuckle through a ball pin.
3. A two-stage drive low height independent suspension system as claimed in claim 1 wherein said push rod is hinged at the middle of said lower cross arm.
4. A two-stage drive low profile independent suspension system as claimed in claim 1 wherein said rocker arm is triangular in shape and three corners of said rocker arm are hinged to said pushrod, hydro-pneumatic spring and vehicle frame respectively.
5. A two-stage drive low height independent suspension system as claimed in claim 4 wherein said vehicle frame has a rocker arm support secured thereto, said rocker arm being pivotally connected to said rocker arm support.
6. A two-stage drive low profile independent suspension system as claimed in claim 1 wherein said frame bottom is cushioned.
7. The two-stage transmission low-height independent suspension system according to claim 1, wherein a hydro-pneumatic spring support is provided on said frame, said hydro-pneumatic spring being hinged to said hydro-pneumatic spring support.
8. The two-stage drive low-height independent suspension system according to claim 1, wherein an oil source port is provided on said hydro-pneumatic spring.
9. A two-stage drive low profile independent suspension system as claimed in claim 1 wherein said upper cross arm is provided with a stop, said stop being located between said knuckle and said hydro-pneumatic spring.
10. Use of a two stage drive low profile independent suspension system according to any of claims 1 to 9 for lowering the height of a heavy chassis and the centre of gravity of a vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211459764.8A CN115742648A (en) | 2022-11-17 | 2022-11-17 | Two-stage transmission low-height independent suspension system and application |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211459764.8A CN115742648A (en) | 2022-11-17 | 2022-11-17 | Two-stage transmission low-height independent suspension system and application |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115742648A true CN115742648A (en) | 2023-03-07 |
Family
ID=85334099
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211459764.8A Pending CN115742648A (en) | 2022-11-17 | 2022-11-17 | Two-stage transmission low-height independent suspension system and application |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115742648A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB297928A (en) * | 1926-08-19 | 1928-10-04 | Francesco Parisi | Improvements in or relating to spring-attachment systems for car-wheels |
| FR776671A (en) * | 1933-10-21 | 1935-01-31 | Combined suspension and damping system for motor cars with independent front wheels | |
| CN102317094A (en) * | 2009-02-13 | 2012-01-11 | 奥迪股份公司 | Have and set to the wheel for motor vehicle suspension wheel hub carriage, that be used to adjust the actuating unit of taking turns elongation and/or camber angle |
| CN102745032A (en) * | 2011-04-20 | 2012-10-24 | 奥迪股份公司 | Wheel suspension for axle of motor vehicle |
| DE102017205258A1 (en) * | 2017-03-28 | 2018-10-04 | Audi Ag | Wheel suspension for a wheel of an axle of a motor vehicle |
| CN112590479A (en) * | 2020-12-24 | 2021-04-02 | 东风越野车有限公司 | Amphibious vehicle overturning suspension structure and amphibious vehicle |
-
2022
- 2022-11-17 CN CN202211459764.8A patent/CN115742648A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB297928A (en) * | 1926-08-19 | 1928-10-04 | Francesco Parisi | Improvements in or relating to spring-attachment systems for car-wheels |
| FR776671A (en) * | 1933-10-21 | 1935-01-31 | Combined suspension and damping system for motor cars with independent front wheels | |
| CN102317094A (en) * | 2009-02-13 | 2012-01-11 | 奥迪股份公司 | Have and set to the wheel for motor vehicle suspension wheel hub carriage, that be used to adjust the actuating unit of taking turns elongation and/or camber angle |
| CN102745032A (en) * | 2011-04-20 | 2012-10-24 | 奥迪股份公司 | Wheel suspension for axle of motor vehicle |
| DE102017205258A1 (en) * | 2017-03-28 | 2018-10-04 | Audi Ag | Wheel suspension for a wheel of an axle of a motor vehicle |
| CN112590479A (en) * | 2020-12-24 | 2021-04-02 | 东风越野车有限公司 | Amphibious vehicle overturning suspension structure and amphibious vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20180009281A1 (en) | Multi-bearing-point independent suspension | |
| US20140131971A1 (en) | Independent suspension system with self-compensated floating swing arm | |
| CN203198673U (en) | Macphersan air suspension | |
| WO2020042366A1 (en) | Mechanical active suspension system | |
| CN201183440Y (en) | Cargo vehicle variable hardness rubber balance suspension apparatus | |
| CN110077184A (en) | A kind of Mecanum wheel omni-directional mobile robots independent suspension structure | |
| CN107415616B (en) | Transverse composite material leaf spring suspension structure | |
| CN107176001B (en) | Automobile shock-absorbing chassis suspension structure | |
| CN111469948A (en) | AGV car | |
| CN113183706B (en) | Double-trailing-arm type active suspension system for full-vector wire control automobile | |
| KR20050113275A (en) | Running gear for a railway vehicle provided with an improved transversal suspension | |
| CN112046527B (en) | Active control type variable-rigidity anti-rolling torsion bar device and rigidity changing method thereof | |
| KR101284346B1 (en) | Active roll control system | |
| CN101177111A (en) | Vehicle complex spring equalization suspension device | |
| CN115742648A (en) | Two-stage transmission low-height independent suspension system and application | |
| CN210027010U (en) | Suspension device and vehicle | |
| CN110077187A (en) | A kind of high bearing capacity vehicle platform | |
| CN107571703B (en) | Single swing arm air suspension system with air bag lifting device for non-driving supporting bridge | |
| CN109130751A (en) | A kind of double gas chamber air suspensions, interconnection suspension system and vehicle | |
| CN115891539B (en) | Low-height independent suspension system of longitudinal hydro-pneumatic spring and application | |
| US11148499B2 (en) | Air rear suspension system for automobile | |
| CN218084987U (en) | Air suspension device and vehicle | |
| Liu | Recent innovations in vehicle suspension systems | |
| CN219339128U (en) | Non-independent oil gas suspension system | |
| CN2761449Y (en) | Bilateral-arm rocker bar type independent suspension |
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 |