CN108223690A - Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row - Google Patents
Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row Download PDFInfo
- Publication number
- CN108223690A CN108223690A CN201810184829.XA CN201810184829A CN108223690A CN 108223690 A CN108223690 A CN 108223690A CN 201810184829 A CN201810184829 A CN 201810184829A CN 108223690 A CN108223690 A CN 108223690A
- Authority
- CN
- China
- Prior art keywords
- balance
- quality
- reciprocating compressor
- opposed
- row
- 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.)
- Granted
Links
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/22—Compensation of inertia forces
- F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The present invention discloses one kind every arranging opposed X-type reciprocating compressor moment of inertia balance mechanism, including bent axle；The trunnion of two crank negative directions of bent axle is gone up respectively sets the first balance weight and the second balance weight, and the quality of the first balance weight and the second balance weight is M1, the radius of gyration be r1；M1r1=msr；One drive gear is set on the trunnion of bent axle；The radial direction of drive gear sets first driven gear, and the first driven gear is engaged with drive gear；At the axis both ends axial distance L of first driven gear, setting is a pair of axisymmetric, diagonally arranged, and the radius of gyration is all r0Third quality and the 4th mass, the quality size of third quality and the 4th mass is m0, respectively it is symmetrically positioned in the axis both sides of the first driven gear：Lr0m0=erms.The one order inertia torque and second-order inertia torque that the present invention realizes every row opposed type X-type reciprocating compressor are zero；The vibration velocity and vibration acceleration for realizing the high reciprocating compressor of X-type multiple row reach minimum.
Description
Technical field
It is more particularly to a kind of every the opposed X-type reciprocating compressor moment of inertia of row the invention belongs to Compressor Technology field
Balance mechanism.
Background technology
X-type reciprocating compressor, exactly four row cylinder-bore axis arrange in cross in horizontal plane or vertical plane, uprightly
Motor drive upright bent axle, so as to which connecting rod and piston be driven to move back and forth in the cylinder, as shown in Figure 1.From reciprocating pressure
The dynamic analysis of contracting machine show that this structure type is for the multiple row high-pressure bench scale reciprocating compressor on naval vessel
One of reciprocal inertia force and its equalising torque type in the best state.The most ideal conditions for reducing or eliminating vibration is reciprocating
One order inertia power, the one order inertia torque of the crank linkage driving system of compressor, the reciprocal inertia of two-stage reciprocating inertia force, second order
Torque is all zero.The most newly developed X-type reciprocating compressor in China, the key performances such as vibration severity and vibration acceleration ratio pass
Two row V-type high-pressure reciprocating compressors of system are much lower, are widely used on many naval vessels that China newly makes.But also not
Higher and higher technical indicator can be met the requirements.
The connecting rod of X-type reciprocating compressor has several arrangement mode, and the connecting rod wherein shown in Fig. 2 (c) is from top under
Putting in order for portion is also a kind of feasible structure.It is referred to as every row opposed type X-type structure, the first order reciprocating inertia force and two
Rank reciprocal inertia force can be balanced by the alternate angle of balance weight and four row alignments.But the first order reciprocating inertia force square and second order are reciprocal
Moment of inertia cannot balance, and cause the vibration severity of reciprocating compressor and vibration acceleration larger.The new solution of demand.
Invention content：
It is an object of the invention to open a kind of every arranging opposed X-type reciprocating compressor moment of inertia balance mechanism, with solution
Certainly above-mentioned technical problem.
To achieve these goals, the present invention adopts the following technical scheme that：
Every arranging opposed X-type reciprocating compressor moment of inertia balance mechanism, including bent axle；Two crank negative directions of bent axle
Trunnion is gone up respectively sets the first balance weight and the second balance weight, and the quality of the first balance weight and the second balance weight is M1, return
It is r to turn radius1；
M1r1=msr
One drive gear is set on the trunnion of bent axle；The radial direction of drive gear sets first driven gear,
First driven gear is engaged with drive gear；At the axis both ends axial distance L of first driven gear, setting is a pair of axisymmetric,
Diagonally arranged, the radius of gyration is all r0Third quality and the 4th mass, the quality size of third quality and the 4th mass is equal
For m0, respectively it is symmetrically positioned in the axis both sides of the first driven gear：
Lr0m0=erms
In formula, ms--- the reciprocating mass of a certain row, kg；
The throw of crankshaft of r --- reciprocating compressor crankshaft, m；
E --- the distance between two adjacent links.
Further, the determining method in third quality and the 4th mass orientation：The crank throw of reciprocating compressor is gone to
The top dead center position of four cylinders, adjustment the first driven gear crank throw reverse position, at this time third quality also adjust to song
Identical orientation namely the 4th mass are turned in opposite position, third quality is consistent with the first balance weight direction；Third quality and
The centrifugal moment vector size of 4th the form of quality is constant, but its direction of rotation is opposite with bent axle direction of rotation.
Further, the second driven gear engaged with drive gear is further included；The setting the in second driven gear one end
Five balance mass blocks and the 6th balance mass block, the other end are equipped with the 7th balance mass block and the 8th balance mass block；Four flat
The quality of weighing apparatus mass block is m00, the radius of gyration be r00, be L to axial distance00；When the crank throw of reciprocating compressor turns
To the 4th cylinder top dead center position when, the 5th balance mass block it is consistent with the direction of the first balance weight, the 7th balance mass block
Direction with the 5th balance mass block is on the contrary, the 6th balance mass block and the 8th balance mass block balance mass block with the 5th respectively
With the 7th balance mass block oriented perpendicular, the 8th balance mass block is consistent with the direction of the connecting rod of the first cylinder, the 6th balance matter
Gauge block and the 8th balance quality Block direction are opposite.
Further, balance quality m00, radius of gyration r00With to axial distance L00With the crank connecting link of reciprocating compressor
Than the reciprocating mass m of λ, column pitch e, throw of crankshaft r and rowsBetween relationship be：
L00m00r00=2 λ erms。
Further, the diameter of the second driven gear and the half that the number of teeth is drive gear.
Further, the diameter of drive gear, modulus and the number of teeth are identical with the first driven gear.
Further, it is connected with the connecting rod of the connecting rod of the first cylinder, the connecting rod of the second cylinder, third cylinder on crank in turn
With the connecting rod of the 4th cylinder；First cylinder is opposed with third cylinder；Second cylinder and the 4th cylinder are opposed.
Relative to the prior art, the invention has the advantages that：Present invention is disclosed reciprocating every row opposed type X-type
The changing rule of the first order reciprocating inertia force square of compressor, has invented the structure of the one order inertia equalising torque, has realized every row
The one order inertia torque and second-order inertia torque of opposed type X type reciprocating compressors are zero；Realize the high reciprocating pressure of X-type multiple row
The vibration velocity and vibration acceleration of contracting machine reach minimum.
Description of the drawings
Fig. 1 is X-type reciprocating compressor outline drawing；
Fig. 2 (a) to Fig. 2 (c) is the connecting rod spread pattern schematic diagram of three kinds of different form X-type reciprocating compressors；Cylinder
Arrangement position, be followed successively by 100,200,300,400 from top to bottom by connecting rod putting in order on crank；
Fig. 3 is every the opposed X-type reciprocating compressor moment of inertia balance mechanism schematic diagram of row：1,2,3,4 are respectively in figure
Cylinder 100,200,300,400 corresponding connecting rods.
Specific embodiment
The index for evaluating a reciprocating compressor power balance quality mainly has：The first order reciprocating inertia force, single order are reciprocal
Moment of inertia, two-stage reciprocating inertia force and two-stage reciprocating inertia force square, usual second-order inertia power be one order inertia power five/
One or so.But the frequency of second-order inertia power effect is 2 times of one order inertia power acting frequency.When designing reciprocating compressor,
One order inertia dynamic balance is pursued first, secondly the balance of two-stage reciprocating inertia force, is single order putting down toward complex moment of inertia third
Weighing apparatus is finally the balance of two-stage reciprocating inertia force square[1]。
There are many connecting rod piston arrangements of X-type reciprocating compressor, wherein shown in attached drawing 2 (c) every row opposed type
Structure is representative.On this connecting rod piston arrangement band after balance weight, the comprehensive one order inertia power of four row and second order are reciprocal
Inertia force can balance；Due to there is a presence of column pitch e, the inertia force of each row effect causes in the axially distinct position of bent axle
The single order and two-stage reciprocating inertia force square that the reciprocating mass respectively arranged and balance weight comprehensive function are formed exist with different numerical value.
Here, the first order reciprocating inertia force value for first defining each row is all
Ⅰ1=msrω2cosθ；
The two-stage reciprocating inertia force value respectively arranged is all
I2=λ msrω2cos2θ；
In above formula, λ --- the ratio between throw of crankshaft and length of connecting rod, generally 0.2 or so.
ms--- the reciprocating mass of a certain row, the reciprocating mass respectively arranged is all equal, kg；
The throw of crankshaft of r --- reciprocating compressor crankshaft, m；
ω --- crankshaft rotation angle speed, 1/s；
θ --- crank relative to each cylinder alignment crank angle, °.
The present invention has found that Fig. 2 (c) shows the one order inertia power every the piston integrated generation of row opposed type X-type by analysis
Moment vector 2e × I1, which is a constant rotation of size in crank up plane or vertical crankshaft axis section
Turn vector, the angular speed of rotation is identical with crankshaft rotation angle velocity magnitude, and numerical value is all ω, and the direction of rotation of the two is opposite.
First as shown in Figure 3 every the trunnion of two crank negative directions of the bent axle 11 for arranging opposed X-type reciprocating compressor
Upper setting balance weight 18 and 18 ', their quality are M1, have：
M1r1=msr
In formula, M1And r1The quality and the radius of gyration of balance weight on bent axle are represented respectively；
msRepresent the reciprocating mass and throw of crankshaft of single-row piston rod conversion respectively with r；
Next, setting a drive gear 17 on the trunnion of bent axle 11, drive gear 17 can be arranged on bent axle
The arbitrary position set in length.In the radial direction of the drive gear 17, another identical with the number of teeth of one diameter, modulus is set
One first driven gear 23, the first driven gear 23 is by 17 engaged transmission of drive gear.It is set on the axis of the first driven gear 23
Two bearings are put, at the both ends axial distance L of axis, setting is a pair of axisymmetric, and diagonally arranged, the radius of gyration is all
r0Quality 22 and quality 22 ', their quality size is m0, the axis both sides of the first driven gear 23 are respectively symmetrically positioned in,
It takes：
Lr0m0=erms
In formula, L, r0And m0Appropriate value can be distinguished, keep total value constant.
E, r and ms--- represent the distance between two adjacent links respectively, throw of crankshaft and a row connecting rod piston it is reciprocal
Quality.
Gear improve quality 22 and the determining method in 22 ' orientation of quality be that the crank throw of reciprocating compressor is gone into cylinder 400
Top dead center position (the top position), as shown in figure 3, reverse position of the first driven gear 23 of adjustment in crank throw, at this time matter
Amount 22 is also adjusted to the orientation namely quality 22 ' identical with crank throw in opposite position (lower end position), quality 22 ' and 18 sides
To consistent.The centrifugal moment vector size that quality 22 and quality 22 ' are formed is constant, but its direction of rotation and bent axle direction of rotation phase
Instead.
The present invention again find, every the second-order inertia torque of row opposed type structure be divided into two orthogonal components and
The constant amount of one size；
The balance of second-order inertia torque can be stated in this way：Second driven gear 19 is set, its diameter and the number of teeth is
The half of drive gear 17, as shown in figure 3, setting two pairs of balance mass blocks 20,20 ' at the both ends of the second driven gear 19
With 21,21 ', balance quality is m00, when the crank throw of reciprocating compressor goes to the top dead center position of the 4th cylinder 400,20
It is consistent with 18 direction, 20 ' and 20 direction on the contrary, 21,21 ' and 20,20 ' oriented perpendicular, 21 ' with the direction one of connecting rod 1
It causes, 21 is opposite with 21 ' directions.Moment components in vertical face can be balanced with 20 and 20 ' balance weight effect square, in water
The balance weight that another moment components in plane can be formed with 21 and 21 ' acts on square to balance.Its direction is with 2 times of angles
The velocity of rotation of speed with crank direction on the contrary, the phase of balance weight as shown in Figure 3.Second order balance quality m00, second order balance
Radius of gyration r00Quality is balanced to axial distance L with second order00With the crank to connecting rod length ratio λ, column pitch e, song of reciprocating compressor
The reciprocating mass m of handle radius r and rowsBetween relationship be：
L00m00r00=2 λ erms
The present invention needs balance gear wheel shaft by bearing with bearing block being connected when practical reciprocating compressor is implemented,
Bearing block is fixedly arranged in crankcase.Gear and bearing are lubricated by being used for the lubricating oil that crankshaft bearing lubricates in crankcase.
Bibliography
[1] Yu Yongzhang etc., positive-displacement reciprocating compressor technical manual, Beijing, China Machine Press, 2001
[2] Lin Mei, Sun Siying, piston type reciprocating compressor principle, Beijing, China Machine Press, 1987.
Claims (7)
1. every arranging opposed X-type reciprocating compressor moment of inertia balance mechanism, which is characterized in that including bent axle (11)；Bent axle
(11) trunnion of two crank negative directions is upper respectively to set the first balance weight (18) and the second balance weight (18 '), the first balance
The quality of weight (18) and the second balance weight (18 ') is M1, the radius of gyration be r1；
M1r1=msr
One drive gear (17) is set on the trunnion of bent axle (11)；The radial direction of drive gear (17) set one first from
Moving gear (23), the first driven gear (23) are engaged with drive gear (17)；The axis both ends of first driven gear (23) it is axial away from
At L, setting is a pair of axisymmetric, diagonally arranged, and the radius of gyration is all r0Third quality (22) and the 4th mass
The quality size of (22 '), third quality (22) and the 4th mass (22 ') is m0, respectively it is symmetrically positioned in the first driven gear
(23) axis both sides：
Lr0m0=erms
In formula, ms--- the reciprocating mass of a certain row, kg；
The throw of crankshaft of r --- reciprocating compressor crankshaft, m；
E --- the distance between two adjacent links.
It is 2. according to claim 1 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
The determining method of third quality (22) and the 4th mass (22 ') orientation：The crank throw of reciprocating compressor is gone into the 4th cylinder
(400) top dead center position adjusts reverse position of the first driven gear (23) in crank throw, and third quality (22) also adjusts at this time
To the orientation identical with crank throw namely the 4th mass (22 ') in opposite position, third quality (22) and the first balance weight (18)
Direction is opposite；The centrifugal moment vector size that third quality (22) and the 4th mass (22 ') are formed is constant, but its direction of rotation with
Bent axle direction of rotation is opposite.
It is 3. according to claim 1 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
Further include the second driven gear (19) engaged with drive gear (17)；The 5th balance of setting in the second driven gear (19) one end
Mass block (20) and the 6th balance mass block (21), the other end are equipped with the 7th balance mass block (20 ') and the 8th balance mass block
(21’)；The quality of four balance mass blocks is m00, the radius of gyration be r00, be L to axial distance00；When reciprocating pressure
When the crank throw of contracting machine goes to the top dead center position of the 4th cylinder (400), the 5th balance mass block (20) and the first balance weight (18)
Direction it is consistent, the 7th balance mass block (20 ') with the 5th balance mass block (20) direction on the contrary, the 6th balance mass block
(21) it hangs down respectively with the 5th balance mass block (20) and the 7th balance mass block (20 ') orientation with the 8th balance mass block (21 ')
Directly, the 8th balance mass block (21 ') it is consistent with the direction of the connecting rod (1) of the first cylinder (100), the 6th balance mass block (21) and
8th balance mass block (21 ') direction is opposite.
It is 4. according to claim 3 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
Balance quality m00, radius of gyration r00With to axial distance L00With the crank to connecting rod length ratio λ, column pitch e, crank of reciprocating compressor
The reciprocating mass m of radius r and rowsBetween relationship be：
L00m00r00=2 λ erms。
It is 5. according to claim 3 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
The diameter and the number of teeth of second driven gear (19) are the half of drive gear (17).
It is 6. according to claim 1 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
Diameter, modulus and the number of teeth of drive gear (17) are identical with the first driven gear (23).
It is 7. according to claim 1 every the opposed X-type reciprocating compressor moment of inertia balance mechanism of row, which is characterized in that
Be connected in turn on crank the connecting rod of the first cylinder (100), the connecting rod of the second cylinder (200), third cylinder (300) connecting rod and
The connecting rod of 4th cylinder (400)；First cylinder (100) is opposed with third cylinder (300)；Second cylinder (200) and the 4th cylinder
(400) it is opposed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810184829.XA CN108223690B (en) | 2018-03-06 | 2018-03-06 | Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of column |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810184829.XA CN108223690B (en) | 2018-03-06 | 2018-03-06 | Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of column |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108223690A true CN108223690A (en) | 2018-06-29 |
| CN108223690B CN108223690B (en) | 2019-07-23 |
Family
ID=62666944
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810184829.XA Expired - Fee Related CN108223690B (en) | 2018-03-06 | 2018-03-06 | Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of column |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108223690B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110630164A (en) * | 2019-08-27 | 2019-12-31 | 浙江立方户外用品股份有限公司 | Novel sun-shading curtain |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2416503A1 (en) * | 1974-04-04 | 1975-10-16 | Rudolf Hintze | Double acting piston compressor with mass balance - for use free of vibration with cooling system of passenger cars |
| CN1220725A (en) * | 1996-04-02 | 1999-06-23 | 帕特里克·迈克尔·克兰斯顿·沃克 | Crankshaft and piston arrangement |
| GB2392210A (en) * | 2002-08-21 | 2004-02-25 | Maxsym Engine Tech Ltd | Arrangement of balancing system and pistons on a crankshaft |
| CN1906413A (en) * | 2004-11-01 | 2007-01-31 | 松下电器产业株式会社 | Reciprocating compressor |
| DE102015104771A1 (en) * | 2015-03-27 | 2016-09-29 | Technische Universität Dresden | Device for mass balance for a reciprocating engine |
| CN107237861A (en) * | 2017-05-17 | 2017-10-10 | 北汽福田汽车股份有限公司 | A kind of vehicle, engine and its crankshaft counterbalance structure |
-
2018
- 2018-03-06 CN CN201810184829.XA patent/CN108223690B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2416503A1 (en) * | 1974-04-04 | 1975-10-16 | Rudolf Hintze | Double acting piston compressor with mass balance - for use free of vibration with cooling system of passenger cars |
| CN1220725A (en) * | 1996-04-02 | 1999-06-23 | 帕特里克·迈克尔·克兰斯顿·沃克 | Crankshaft and piston arrangement |
| GB2392210A (en) * | 2002-08-21 | 2004-02-25 | Maxsym Engine Tech Ltd | Arrangement of balancing system and pistons on a crankshaft |
| CN1906413A (en) * | 2004-11-01 | 2007-01-31 | 松下电器产业株式会社 | Reciprocating compressor |
| DE102015104771A1 (en) * | 2015-03-27 | 2016-09-29 | Technische Universität Dresden | Device for mass balance for a reciprocating engine |
| CN107237861A (en) * | 2017-05-17 | 2017-10-10 | 北汽福田汽车股份有限公司 | A kind of vehicle, engine and its crankshaft counterbalance structure |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110630164A (en) * | 2019-08-27 | 2019-12-31 | 浙江立方户外用品股份有限公司 | Novel sun-shading curtain |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108223690B (en) | 2019-07-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4138897A (en) | Balanced crankshaft mechanism for the two piston Stirling engine | |
| US4966042A (en) | Balanced reciprocating machines | |
| CN107237861A (en) | A kind of vehicle, engine and its crankshaft counterbalance structure | |
| JPS61157726A (en) | Multicylinder internal combustion piston engine | |
| EP0890040B1 (en) | Crankshaft and piston arrangement | |
| CN108223690B (en) | Every the opposed X-type reciprocating compressor moment of inertia balance mechanism of column | |
| CN106122370B (en) | A kind of balance system of single cylinder diesel | |
| US4694785A (en) | Piston apparatus | |
| CN111761852B (en) | Novel lightweight complete dynamic balance mode and device for double-shaft four-point high-speed press | |
| CN108443408B (en) | Adjacent row opposite X-type reciprocating compressor inertia moment balancing mechanism | |
| CN108708934A (en) | Two cylinder arbor system balance shock system | |
| CN2035817U (en) | Multicylinder diesel engine balanced means | |
| CN108397515B (en) | The one order inertia dynamic balance mechanism of single-row reciprocating compressor | |
| CN116480678A (en) | Bent axle system structure of V-shaped engine and full balance process | |
| CN108443409B (en) | Two-end row opposed X-type reciprocating compressor inertia moment balancing mechanism | |
| CN105508502B (en) | A kind of five cylinder Diesel engine crankshaft counterbalance systems | |
| JP2004239182A (en) | Engine piston drive mechanism | |
| CN110295995B (en) | Structure capable of realizing full balance and multi-cylinder combined piston engine | |
| EP0058475A1 (en) | Improvements in engine balancing | |
| CN1894505A (en) | Crank gear for a reciprocating compressor | |
| CN205908693U (en) | Balanced system of single cylinder diesel | |
| CN207073544U (en) | Single-cylinder engine | |
| CN220060233U (en) | V-shaped engine crankshaft system structure | |
| EP2679782B1 (en) | Internal combustion engine with 'V' configuration of the cylinders | |
| CN219605406U (en) | Inverted V-shaped low-vibration two-cylinder engine |
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 | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190723 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |