CN203868191U - Double-row forward inclined blade type hydraulic retarder - Google Patents
Double-row forward inclined blade type hydraulic retarder Download PDFInfo
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- CN203868191U CN203868191U CN201420128680.0U CN201420128680U CN203868191U CN 203868191 U CN203868191 U CN 203868191U CN 201420128680 U CN201420128680 U CN 201420128680U CN 203868191 U CN203868191 U CN 203868191U
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Abstract
The utility model relates to a double-row forward inclined blade type hydraulic retarder which comprises a gearbox body, a stator, a rotor and blades. The double-row forward inclined blade type hydraulic retarder is characterized in that double chambers of the stator and double chambers of the rotor are arranged in corresponding concentric circles respectively to form a double-row double-chamber hydraulic retarding structure, the outer circle of the stator is fixed to the inner wall of the gearbox body, the annular first row of working chambers and the annular second row of working chambers are arranged on the concentric circle of the stator, the first row of working chambers and the second row of working chambers are also arranged on the concentric circle of the rotor corresponding to those of the stator and are buckled with those of the stator, and blades are arranged in the first row of working chambers and the second row of working chambers of the stator and in the first row of working chambers and the second row of working chambers of the rotor respectively. The hydraulic retarder has the advantages that the double-row working chamber (including round chambers and square chambers) hydraulic retarding structure is adopted, the blades are installed in all the working chambers, a high braking torque can be obtained with a small structural size, axial size is small, oil pumping capacity is high, and the braking torque is high. When the hydraulic retarder is applied to a highway passenger vehicle or a large-tonnage truck, the vehicles can travel downhill at a safe and constant speed.
Description
Technical field
The utility model belongs to Vehicular brake device, relates in particular to a kind of double forward blade hydrodynamic retarder that is applicable to highway passenger vehicle and heavy truck downhill retardation.
Background technique
Car deceleration in travelling is even stopped, make the car speed of descent run keep stable, and make the automobile of stagnation of movement keep motionless, these effects are referred to as automobile brake.In order to guarantee vehicle driving safety, on vehicle, braking system is absolutely necessary.According to the difference of function, the braking system on vehicle can be divided into service braking sytem, parking braking system, the secondary brakes auxiliary braking system of unifying.First three function of planting braking system is mainly that the vehicle deceleration that makes to travel even stops or allowing the vehicle having stopped being anchored in original place, and service brake, parking braking and secondary brake system break used is nearly all friction brake.Flourish along with motor transport service, require vehicle to have higher efficiency of operation, vehicle-mounted quality, Vehicle Speed and operating range all increase substantially, again because China is vast in territory with a varied topography, a lot of places are all to take mountain area and undulating topography as main, Vehicle Driving Cycle is when this landform, the situation of descending is a lot, if utilize friction brake to carry out vehicle-speed limit to vehicle under this kind of road conditions, not only expending driver's muscle power also can cause friction brake to produce amount of heat and deterioration because of working long hours, when serious, cause braking failure, threaten traffic safety.In order to address this problem, during restriction vehicle descending, the speed of a motor vehicle guarantees that the various auxiliary brake of vehicle of traffic safety develop rapidly.State compulsion operative norm < < GB7258-2012 Motor Vehicle safe and technical specification > > and the division of traffic transport industry standard < < JT/T325-2010 operating passenger car type and ranking > > are to large-scale extra bus, heavy duty truck, retarder is installed for special operating vehicle and Dangerous Goods Transport vehicle or other auxiliary brakes have been made clear and definite regulation.Retarder is exactly a kind of auxiliary brake of vehicle producing under this technical requirements.
Retarder is as a kind of complemental brake system, when car deceleration or lower long slope, can make automobile balance slow down or maintain lower speed, alleviate the impact of automotive transmission, improve the stationarity of automobile in moderating process, reduce wearing and tearing and the heating of break, and then extend the working life of break, increase the Security of Vehicle Driving Cycle, the economic loss that reduces the upkeep cost of automobile and stop transport and cause because of vehicle.
Hydrodynamic retarder and electric eddy current retarder are the retarders often using now, along with vehicle technology is to safer, more high power, more heavy load, faster overall trip speed, longer activity duration future development, vehicle braking performances is had higher requirement, electric eddy current retarder is because of the limitation of structure and principle, be difficult to meet this requirement completely, technical development and the use on vehicle have all been subject to great limitation.
The braking principle of hydrodynamic retarder is hydraudynamic drive, the braking moment formula of retarder according to retarder the setting type on vehicle different, its basic calculating formula is: M=λ ρ gD
5n
2, in formula: D-rotor Efficient Cycle circular diameter, n-rotor speed, λ-braking moment coefficient, ρ-flowing medium density, g-gravity accleration.Five powers of hydrodynamic retarder retarding torque and its rotor speed square and circulate circle diameter are directly proportional, so its braking effect in high vehicle speeds is obvious, and utilize the hydrodynamic retarder of reduced size can obtain larger braking torque.Advantage based on above, hydrodynamic retarder is widely used on heavy type and High-Powered Vehicle.
The hydraulic speed buffer structure of installing in different vehicle is roughly the same, generally stator, rotor, active chamber, input shaft, heat exchanger, fuel reserve tank and housing, consists of.Its mounting type be generally divided into transmission shaft series winding and and connect two kinds, can be in the forward and backward installation of speed changer during series winding, if take and connect, retarder and speed changer are made an integral body and are installed.For the vehicle with automatic transmission being equipped with fluid torque converter, former transmission system has been equipped with the parts such as oil storage tank, oil pump and radiator, and therefore, on the passenger vehicle of automatic transmission and cargo vehicle, hydrodynamic retarder to be installed more convenient being furnished with.
During retarder work, pressurized air enters fuel reserve tank through solenoid valve, and the fluid in fuel reserve tank is compressed into retarder through oil circuit, retarder is started working, rotor drives fluid to rotate around axis, and meanwhile, fluid moves along direction blade, get rid of to stator, stator vane produces reaction to fluid, and fluid outflow stator goes back to impact rotor again, so just forms the resisting moment to rotor, hinder the rotation of rotor, thereby realize the decelerating effect to vehicle.It is poor that working solution makes to import and export mineralization pressure in movement process, and oil circulation flows, and during by heat exchanger, heat is taken away by the cooling water from engine-cooling system.
Hydrodynamic retarder relies on hydraulic transmission oil transmitting torque, do not have mechanical rigid to connect, mechanical wear and vibration have been avoided, can improve the stability of operation and the comfort level of driving, radiator can distribute the heat producing in hydrodynamic retarder braking process in time, so hydrodynamic retarder can provide the braking moment of vehicle operating needs continuously.During lower long slope, in the situation that Service Brake does not participate in braking, depend merely on hydrodynamic retarder and just can make vehicle travel with a certain safe constant-velocity.
In order to adapt to social development needs, the carrying capacity of load-carrying vehicle continues to increase, and its operate power is also constantly increasing, in order to guarantee that vehicle driving safety just needs the larger hydrodynamic retarder that can hold.Conventional hydrodynamic retarder can hold in order to increase it now, conventionally adopt the two-chamber form being symmetrically arranged to increase retarding torque (see figure 10), its basic structure is that two active chambers are symmetrically arranged, and two active chambers are measure-alike, and blade quantity corresponding in two chambeies is also identical.Although the two-chamber form being symmetrically arranged has increased retarding torque, the vehicle space taking also strengthens, and has increased difficulty to the Design and manufacture of vehicle.
In sum, in order to increase the application area of hydrodynamic retarder, just must develop the large hydrodynamic retarder of the little energy appearance of size.
Model utility content
The purpose of this utility model is to overcome the technical deficiency of traditional hydrodynamic retarder, a kind of double forward blade hydrodynamic retarder is provided, can hold large, installation dimension is little, fill oil extraction speed fast, take into account and can hold and bulk two aspect requirements, can not only hold large and can accomplish that size is little, be applicable to very much powerful truck and motorbus and use.
The utility model for achieving the above object, by the following technical solutions: a kind of double forward blade hydrodynamic retarder, comprise gear box, stator, rotor and blade, it is characterized in that, the two-chamber of described stator and rotor is separately positioned on separately and forms double two-chamber hydrodynamic retarding structure in concentric circle, described stator cylindrical and gear box inwall are fixed, described stator is respectively equipped with annular first row active chamber and annular second row active chamber on concentric circle, described first row active chamber is located at the large radius of stator, its shape of cross section semicircular in shape, second row active chamber is located at stator minor radius place, its shape of cross section is rectangular, the corresponding stator of described rotor is also provided with first row active chamber and second row active chamber, and fasten and arrange with stator, in the first row active chamber of described stator and rotor and second row active chamber, be respectively equipped with blade, described stator supports by being arranged on epitrochanterian bearing, described rotor is connected with splined shaft by spline, on the first row active chamber of described stator, have oil outlet, the second row active chamber middle part of described stator has filler opening.
The circulate circle diameter of the first row active chamber of described stator and rotor is 260mm～385mm, and the second row active chamber circulate circle diameter of described stator and rotor is half of first row active chamber circulate circle diameter.
The blade quantity of described first row work intracavitary unit is 30～43, and blade pitch angle is 32 °～40 °, and the blade quantity of second row work intracavitary unit is 15～22, and its tilt angle is 32 °～40 °, and the true dip direction of two active chamber blades is identical.
The filler opening quantity of described stator is 6～8, and diameter is 12mm～16mm, and oil outlet quantity is 8～10, and diameter is 8mm～12mm.
The first row active chamber of described stator and rotor and the spacing between second row active chamber are less than the spacing between two adjacent blades, and described stator vane has semicircle breach.
Between described stator and rotor 2, be provided with the axial assembly building distance of 2.5mm～3.5mm.
Described stator outer rim is provided with spline and pegs graft fixing with the inner spline groove of gear box inwall.
Beneficial effect: can hold the shortcoming little, axial dimension is large in order to overcome traditional hydrodynamic retarder, the utility model has adopted the hydraulic speed buffer structure of double active chamber, in retarder, there are two row's active chambers: round chamber and rectangular cavity, and blade is all installed, can obtain larger retarding torque with less physical dimension.The hydraulic speed buffer structure that the utility model proposes is simple, and axial dimension is little, and pumping ability is strong, and braking torque is large.When the utility model is applied to highway passenger vehicle and large-tonnage cargo vehicle, can make vehicle with a certain safety speed constant speed lower long slope.
Figure of description
Fig. 1 is double forward blade hydrodynamic retarder assembling schematic diagram;
Fig. 2 is rotor front view;
Fig. 3 is rotor A-A sectional view;
Fig. 4 is rotor B-B sectional view;
Fig. 5 is rotor C-C sectional view;
Fig. 6 is stator front view;
Fig. 7 is stator D-D sectional view;
Fig. 8 is stator E-E sectional view;
Fig. 9 is stator F-F sectional view;
Figure 10 is traditional two-chamber hydraulic speed buffer structure schematic diagram.
In figure, 1. gear box, 2. rotor, 3. splined shaft, 4. second row active chamber, 5. first row active chamber, 6. oil outlet, 7. stator, 8. filler opening, 9. bearing (ball) cover, 10. screw, 11. seal rings, 12. bearings, 13. rotor round chamber blades, 14. rotor rectangular cavity blades, 15. stator round chamber blades, the semicircle breach of 16. blades, 17. stator rectangular cavity blades, 18. traditional two-chamber hydrodynamic retarder stators, 19. traditional two-chamber hydrodynamic retarder rotors, 20. traditional two-chamber hydrodynamic retarder rotors.
In Figure 10,1-1. tradition two-chamber hydrodynamic retarder the first chamber, 1-2. tradition two-chamber hydrodynamic retarder the second chamber.
Embodiment
Below in conjunction with preferred embodiment, describe embodiment of the present utility model in detail.
A kind of double forward blade hydrodynamic retarder, comprise gear box, stator 7, rotor 2 and blade, the two-chamber of described stator and rotor is separately positioned on separately and forms double two-chamber hydrodynamic retarding structure in concentric circle, described stator cylindrical and gear box inwall are fixed, described stator is respectively equipped with annular first row active chamber 5 and annular second row active chamber 4 on concentric circle, described first row active chamber is located at the large radius of stator, its shape of cross section semicircular in shape, second row active chamber is located at stator minor radius place, its shape of cross section is rectangular, the corresponding stator of described rotor is also provided with first row active chamber and second row active chamber, and fasten and arrange with stator, in described first row active chamber and second row active chamber, be respectively equipped with blade, described stator is by being arranged on epitrochanterian bearing 12 supportings, described rotor is connected with splined shaft 3 by spline, on the first row active chamber of described stator, have oil outlet, the second row active chamber middle part of described stator has filler opening.The circulate circle diameter of the first row active chamber of described stator and rotor is 260mm～385mm, and the second row active chamber circulate circle diameter of described stator and rotor is half of first row active chamber circulate circle diameter.The blade quantity of described first row work intracavitary unit is 30～43, and blade pitch angle is 32 °～40 °, and the blade quantity of second row work intracavitary unit is 15～22, and its tilt angle is 32 °～40 °, and the true dip direction of two active chamber blades is identical.The filler opening quantity of described stator is 6～8, and diameter is 12mm～16mm, and oil outlet quantity is 8～10, and diameter is 8mm～12mm.The first row active chamber of described stator and rotor and the spacing between second row active chamber are less than the spacing between two adjacent blades, and on stator round chamber blade 15 and stator rectangular cavity blade 17, all have semicircle breach 16, can guarantee that like this oil-feed and oil extraction process implementation fill rapidly oil extraction equably.
Embodiment 1
As shown in Figure 1, hydrodynamic retarder is mainly comprised of stator 7 and rotor 2, rotor 2 is connected with splined shaft 3 by spline, and splined shaft 3 is connected with the rotary component of vehicle drive system by key, and the spline of stator 7 by outer rim is arranged in gear box 1 and maintains static.In order further to reduce axial dimension, on gear box 1, design a barrel shaped structure and be processed with internal spline, be convenient to retarder and install.Stator 7 is supported by bearing 12, and bearing 12 is arranged on rotor 2, and the left side utilizes the shaft shoulder of rotor 2 to position, and the right utilizes bearing (ball) cover 9 to position.Bearing (ball) cover 9 is fixed on stator 7 by screw 10, and seal ring 11 is arranged in bearing (ball) cover 9 for sealing.The axial assembly building distance that has Δ=2.5mm between rotor 2 and stator 7.Vehicle is when descent run, hydraulic transmission oil is pumped into by oil pump from filler opening 8, be full of rapidly two active chambers, engine idle, car load gravity drags transmission shaft rotation along the component of ramp direction, transmission shaft rotates and drives splined shaft 3 and rotor 2 rotations, the working solution that the rotor round chamber blade 13 of rotor 2 and rotor rectangular cavity blade 14 stir in hydrodynamic retarder cavity, make working solution impact stator round chamber blade 15 and stator rectangular cavity blade 17, at working solution and rotor round chamber blade 13, in the interaction process of rotor rectangular cavity blade 14, working solution has produced torque to rotor blade, this torque is contrary with the torque direction that car load partical gravity produces, thereby make vehicle deceleration or constant speed drive.
As shown in Fig. 2,3,4,5, the circulate circle diameter D of rotor 2
r1=260mm, compare with the structure of common enclosed hydrodynamic retarder, rotor 2 has two row's active chambers: annular first row active chamber 5(round chamber) and annular second row active chamber 4(rectangular cavity), in its round chamber, be provided with 33 tilt angle and be the blade 13 of 34 °, in rectangular cavity, be provided with 17 tilt angle and be the blade 14 of 34 °, the true dip direction of blade is identical with the sense of rotation of rotor.
As shown in Fig. 6,7,8,9, the circulate circle diameter D of stator 7
r1=260mm, identical with rotor 2, on it, also there are two row's active chambers: round chamber and rectangular cavity, in its round chamber, be provided with 37 tilt angle and be the blade 15 of 34 °, in rectangular cavity, be provided with nineteen tilt angle and be the blade 17 of 34 °, its true dip direction is consistent with the true dip direction of rotor blade 13,14, at its rectangular cavity middle part, has the filler opening 8 that 6 diameters are 12mm, at its round chamber, near radius biggest place, has the oil outlet 6 that 8 diameters are 8mm.
Embodiment 2
As shown in Figure 1, hydrodynamic retarder is mainly comprised of stator 7 and rotor 2, rotor 2 is connected with splined shaft 3 by spline, and splined shaft 3 is connected with the rotary component of vehicle drive system by key, and the spline of stator 7 by outer rim is arranged in gear box 1 and maintains static.In order further to reduce axial dimension, on gear box 1, design a barrel shaped structure and be processed with internal spline, be convenient to retarder and install.Stator 7 is supported by bearing 12, and bearing 12 is arranged on rotor 2, and the left side utilizes the shaft shoulder of rotor 2 to position, and the right utilizes bearing (ball) cover 9 to position.Bearing (ball) cover 9 is fixed on stator 7 by screw 10, and seal ring 11 is arranged in bearing (ball) cover 9 for sealing.The axial assembly building distance that has Δ=3mm between rotor 2 and stator 7.Vehicle is when descent run, hydraulic transmission oil is pumped into by oil pump from filler opening 8, be full of rapidly two active chambers, engine idle, car load gravity drags transmission shaft rotation along the component of ramp direction, transmission shaft rotates and drives splined shaft 3 and rotor 2 rotations, the blade 13 of rotor 2 and 14 working solutions that stir in hydrodynamic retarder cavity, make working solution impact the blade 15 and 17 of stator, at working solution and rotor blade 13, in 14 interaction process, working solution has produced torque to rotor blade, this torque is contrary with the torque direction that car load partical gravity produces, thereby make vehicle deceleration or constant speed drive.
As shown in Fig. 2,3,4,5, the circulate circle diameter D of rotor 2
r1=300mm, compare with the structure of common enclosed hydrodynamic retarder, rotor 2 has two row's active chambers: annular first row active chamber 5(round chamber) and annular second row active chamber 4(rectangular cavity), in its round chamber, be provided with 32 tilt angle and be the blade 13 of 36 °, in rectangular cavity, be provided with 16 tilt angle and be the blade 14 of 36 °, the true dip direction of blade is identical with the sense of rotation of rotor.
As shown in Fig. 6,7,8,9, the circulate circle diameter D of stator 7
r1=300mm, identical with rotor 2, on it, also there are two row's active chambers: round chamber and rectangular cavity, in its round chamber, be provided with 37 tilt angle and be the blade 15 of 36 °, in rectangular cavity, be provided with 18 tilt angle and be the blade 17 of 36 °, its true dip direction is consistent with the true dip direction of rotor blade 13,14, at its rectangular cavity middle part, has the filler opening 8 that 6 diameters are 12mm, at its round chamber, near radius biggest place, has the oil outlet 6 that 8 diameters are 10mm.
Embodiment 3
As shown in Figure 1, hydrodynamic retarder is mainly comprised of stator 7 and rotor 2, rotor 2 is connected with splined shaft 3 by spline, and splined shaft 3 is connected with the rotary component of vehicle drive system by key, and the spline of stator 7 by outer rim is arranged in gear box 1 and maintains static.In order further to reduce axial dimension, on gear box 1, design a barrel shaped structure and be processed with internal spline, be convenient to retarder and install.Stator 7 is supported by bearing 12, and bearing 12 is arranged on rotor 2, and the left side utilizes the shaft shoulder of rotor 2 to position, and the right utilizes bearing (ball) cover 9 to position.Bearing (ball) cover 9 is fixed on stator 7 by screw 10, and seal ring 11 is arranged in bearing (ball) cover 9 for sealing.The axial assembly building distance that has Δ=3mm between rotor 2 and stator 7.Vehicle is when descent run, hydraulic transmission oil is pumped into by oil pump from filler opening 8, be full of rapidly two active chambers, engine idle, car load gravity drags transmission shaft rotation along the component of ramp direction, transmission shaft rotates and drives splined shaft 3 and rotor 2 rotations, the blade 13 of rotor 2 and 14 working solutions that stir in hydrodynamic retarder cavity, make working solution impact the blade 15 and 17 of stator, at working solution and rotor blade 13, in 14 interaction process, working solution has produced torque to rotor blade, this torque is contrary with the torque direction that car load partical gravity produces, thereby make vehicle deceleration or constant speed drive.
As shown in Fig. 2,3,4,5, the circulate circle diameter D of rotor 2
r1=320mm, compare with the structure of common enclosed hydrodynamic retarder, rotor 2 has two row's active chambers: annular first row active chamber 5(round chamber) and annular second row active chamber 4(rectangular cavity), in its round chamber, be provided with 35 tilt angle and be the blade 13 of 40 °, in rectangular cavity, be provided with 17 tilt angle and be the blade 14 of 40 °, the true dip direction of blade is identical with the sense of rotation of rotor.
As shown in Fig. 6,7,8,9, the circulate circle diameter D of stator 7
r1=320mm, identical with rotor 2, on it, also there are two row's active chambers: round chamber and rectangular cavity, in its round chamber, be provided with 39 tilt angle and be the blade 15 of 40 °, in rectangular cavity, be provided with 20 tilt angle and be the blade 17 of 40 °, its true dip direction is consistent with the true dip direction of rotor blade 13,14, at its rectangular cavity middle part, has the filler opening 8 that 8 diameters are 12mm, at its round chamber, near radius biggest place, has the oil outlet 6 that 10 diameters are 10mm.
The above, be only preferred embodiment of the present utility model, not structure of the present utility model done to any pro forma restriction.Any simple modification, equivalent variations and modification that every foundation technical spirit of the present utility model is done above embodiment, all still belong in the scope of technical solutions of the utility model.
Claims (7)
1. a double forward blade hydrodynamic retarder, comprises gear box, stator, rotor and blade, it is characterized in that: the two-chamber of described stator and rotor is separately positioned on separately and forms double two-chamber hydrodynamic retarding structure in concentric circle; Described stator cylindrical and gear box inwall are fixed, described stator is respectively equipped with annular first row active chamber and annular second row active chamber on concentric circle, described first row active chamber is located at the large radius of stator, its shape of cross section semicircular in shape, second row active chamber is located at stator minor radius place, and its shape of cross section is rectangular; The corresponding stator of described rotor is also provided with first row active chamber and second row active chamber, and fastens and arrange with stator; In the first row active chamber of described stator and rotor and second row active chamber, be respectively equipped with blade; Described stator supports by being arranged on epitrochanterian bearing, and described rotor is connected with splined shaft by spline; On the first row active chamber of described stator, have oil outlet, the second row active chamber middle part of described stator has filler opening.
2. double forward blade hydrodynamic retarder according to claim 1, it is characterized in that: the circulate circle diameter of the first row active chamber of described stator and rotor is 260mm～385mm, the second row active chamber circulate circle diameter of described stator and rotor is half of first row active chamber circulate circle diameter.
3. double forward blade hydrodynamic retarder according to claim 1 and 2, it is characterized in that: the blade quantity of described first row work intracavitary unit is 30～43, blade pitch angle is 32 °～40 °, the blade quantity of second row work intracavitary unit is 15～22, its tilt angle is 32 °～40 °, and the true dip direction of two active chamber blades is identical.
4. double forward blade hydrodynamic retarder according to claim 3, is characterized in that: the filler opening quantity of described stator is 6～8, and diameter is 12mm～16mm, and oil outlet quantity is 8～10, and diameter is 8mm～12mm.
5. double forward blade hydrodynamic retarder according to claim 4, it is characterized in that: the first row active chamber of described stator and rotor and the spacing between second row active chamber are less than the spacing between two adjacent blades, and described stator vane has semicircle breach.
6. double forward blade hydrodynamic retarder according to claim 5, is characterized in that: the axial assembly building distance that is provided with 2.5mm～3.5mm between described stator and rotor.
7. double forward blade hydrodynamic retarder according to claim 6, is characterized in that: described stator outer rim is provided with spline and pegs graft fixing with the inner spline groove of gear box inwall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420128680.0U CN203868191U (en) | 2014-03-21 | 2014-03-21 | Double-row forward inclined blade type hydraulic retarder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420128680.0U CN203868191U (en) | 2014-03-21 | 2014-03-21 | Double-row forward inclined blade type hydraulic retarder |
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| CN203868191U true CN203868191U (en) | 2014-10-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420128680.0U Withdrawn - After Issue CN203868191U (en) | 2014-03-21 | 2014-03-21 | Double-row forward inclined blade type hydraulic retarder |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103821851A (en) * | 2014-03-21 | 2014-05-28 | 中国人民解放军军事交通学院 | Double row forward inclining vane hydraulic retarder |
| CN105757145A (en) * | 2016-05-18 | 2016-07-13 | 苏州特速安机电科技有限公司 | Hydraulic retarder |
| CN108343689A (en) * | 2018-02-10 | 2018-07-31 | 北京工业大学 | A kind of Retarder bridge of built-in double water pump |
| CN111673570A (en) * | 2020-08-04 | 2020-09-18 | 招远东威金属工艺家具有限公司 | Metal desktop polishing device and using method thereof |
-
2014
- 2014-03-21 CN CN201420128680.0U patent/CN203868191U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103821851A (en) * | 2014-03-21 | 2014-05-28 | 中国人民解放军军事交通学院 | Double row forward inclining vane hydraulic retarder |
| CN103821851B (en) * | 2014-03-21 | 2016-04-06 | 中国人民解放军军事交通学院 | Double forward blade hydrodynamic retarder |
| CN105757145A (en) * | 2016-05-18 | 2016-07-13 | 苏州特速安机电科技有限公司 | Hydraulic retarder |
| CN108343689A (en) * | 2018-02-10 | 2018-07-31 | 北京工业大学 | A kind of Retarder bridge of built-in double water pump |
| CN111673570A (en) * | 2020-08-04 | 2020-09-18 | 招远东威金属工艺家具有限公司 | Metal desktop polishing device and using method thereof |
| CN111673570B (en) * | 2020-08-04 | 2021-03-23 | 招远东威金属工艺家具有限公司 | Metal desktop polishing device and using method thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141008 Effective date of abandoning: 20160406 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |