CN109114051B - Variable load tool - Google Patents
Variable load tool Download PDFInfo
- Publication number
- CN109114051B CN109114051B CN201810986441.1A CN201810986441A CN109114051B CN 109114051 B CN109114051 B CN 109114051B CN 201810986441 A CN201810986441 A CN 201810986441A CN 109114051 B CN109114051 B CN 109114051B
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- Prior art keywords
- pressure
- shaft
- oil
- hole
- oil outlet
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/615—Filtering means
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
The invention discloses a variable load tool, and belongs to the field of testing devices. This become load frock includes the bearing piece, pressure shaft and hydraulic loading system, be provided with the pressure chamber of a cylindricality in the bearing piece, still be equipped with the shaft hole on the bearing piece, the inlet port, the oil outlet, the shaft hole is located the one end of pressure chamber, the pressure shaft cartridge is in the shaft hole, the first end of pressure shaft is equipped with the shaft coupling, the second end of pressure shaft is provided with the outward flange, inlet port and shaft hole are located the opposite both sides of outward flange respectively, inlet port and oil outlet are located the homonymy of outward flange, after to the pressure chamber pressurization, the outward flange can compress tightly on the inner wall of pressure chamber. When the grinding is carried out, the pressure shaft can be connected with the output shaft of the equipment to be ground through the coupler, the friction force between the outer flange and the inner wall of the pressure cavity is equivalent to the load acting on the output shaft of the equipment to be ground, so that the working condition during grinding is the same as the working condition during actual use, the grinding effect is improved, and the grinding time is shortened.
Description
Technical Field
The invention relates to the field of testing devices, in particular to a variable load tool.
Background
In industrial production, a plurality of devices need to be run-in after being manufactured and before being used formally, so that the devices are more stable in the formal use.
Taking the gear box as an example, after the manufacture is completed, the input shaft of the gear box is usually driven to rotate by adopting power of a motor and the like, so that the gears in the gear box run and are in running-in.
Because the gear box is at the during operation, except that the input shaft has power input, still have the load on the output shaft, and during running-in, the output shaft is in idle state, and this makes the operating mode when the gear box grinds different with the operating mode when the gear box actually uses, leads to the running-in effect not good, and the running-in time is long.
Disclosure of Invention
The embodiment of the invention provides a variable-load tool which can improve the running-in effect and shorten the running-in time. The technical scheme is as follows:
the embodiment of the invention provides a variable load tool, which comprises a bearing block, a pressure shaft and a hydraulic loading system, wherein a cylindrical pressure cavity is arranged in the bearing block, a shaft hole, an oil inlet hole and an oil outlet hole are also arranged on the bearing block, the shaft hole, the oil inlet hole and the oil outlet hole are all communicated with the outer surfaces of the pressure cavity and the bearing block, the shaft hole is positioned at one end of the pressure cavity, the axis of the shaft hole is parallel to the axis of the pressure cavity, the cross section of the shaft hole is smaller than that of the pressure cavity, the pressure shaft is inserted in the shaft hole, the first end of the pressure shaft is exposed out of the bearing block, a coupler is arranged at the first end of the pressure shaft, the second end of the pressure shaft is positioned in the pressure cavity, an outer flange extending outwards along the radial direction of the pressure shaft is arranged at the second end of the pressure shaft, the periphery wall of outward flange with the inner wall sliding seal of pressure chamber, the inlet port with the shaft hole is located respectively the opposite both sides of outward flange, the inlet port with the oil outlet is located the homonymy of outward flange, hydraulic loading system with the inlet port with the oil outlet intercommunication, hydraulic loading system is configured as to be controllablely right the pressure chamber pressurization, and make the pressure of pressure chamber is invariable.
Optionally, the pressure-bearing block comprises a block-shaped body and a stop block, the block is detachably connected with the stop block, the stop block is located at one end of the pressure chamber, the orthographic projection of the pressure chamber on the stop block is located in the end face, close to the pressure chamber, of the stop block, and the shaft hole is located on the stop block.
Optionally, a sealing ring is disposed between the block body and the stopper.
Optionally, the stop is threadedly connected with the block body.
Optionally, the hydraulic loading system includes an oil tank, a loading pump, a check valve, a pressure gauge and a stop valve, an oil inlet of the loading pump is communicated with the oil tank, an oil outlet of the loading pump is communicated with an oil inlet of the check valve, an oil outlet of the check valve is communicated with the oil inlet hole, the oil outlet of the check valve is further connected with the pressure gauge, the oil outlet hole is communicated with the oil inlet of the stop valve, and the oil outlet of the stop valve is communicated with the oil tank.
Optionally, the hydraulic loading system further includes an overflow valve, an oil inlet and a pilot oil port of the overflow valve are both communicated with an oil outlet of the loading pump, and an oil outlet of the overflow valve is communicated with the oil tank.
Optionally, the hydraulic loading system further comprises a filter connected between an oil outlet of the loading pump and an oil inlet of the one-way valve.
Optionally, a liquid level meter is arranged in the oil tank.
Optionally, an air filter is arranged on the oil tank.
Optionally, an oil drain valve is arranged on the oil tank.
The technical scheme provided by the embodiment of the invention has the following beneficial effects: the pressure cavity is arranged in the pressure bearing block, and the oil inlet and the oil outlet are arranged on the pressure bearing block, so that the pressure cavity can be pressurized through a hydraulic loading system. Through set up the shaft hole on the bearing block, with pressure shaft cartridge to the shaft hole in, because the epaxial outward flange that is provided with of pressure, the outer flange slides with the inner wall of pressure chamber and seals, the cross section in shaft hole is less than the cross section of pressure chamber, inlet port and shaft hole are located the opposite both sides of outward flange respectively, inlet port and oil outlet are located the homonymy of outward flange, consequently, after pressurizeing the pressure chamber, the outward flange can compress tightly on the inner wall of pressure chamber, and the pressure in the pressure chamber is big more, the packing force that the outward flange used on the inner wall of pressure chamber. Friction is generated between the outer flange and the inner wall of the pressure chamber, and the magnitude of the friction can be adjusted by varying the magnitude of the pressing force of the outer flange against the inner wall of the pressure chamber. When the grinding is carried out, the pressure shaft can be connected with an output shaft of equipment to be ground through a coupler on the pressure shaft, the friction force between the outer flange and the inner wall of the pressure cavity is equivalent to the load acting on the output shaft of the equipment to be ground, the size of the load can be changed by changing the size of the friction force, the working condition during grinding is the same as the working condition during actual use, therefore, the grinding effect is improved, and the grinding time is shortened.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a structural diagram of a variable load tool according to an embodiment of the present invention;
fig. 2 is a schematic diagram of a hydraulic loading system according to an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
Fig. 1 is a structural diagram of a variable load tool according to an embodiment of the present invention, and as shown in fig. 1, the variable load tool includes a pressure block 10, a pressure shaft 20, and a hydraulic loading system 30.
A cylindrical pressure chamber 11a is provided in the pressure block 10. The pressure bearing block 10 is also provided with a shaft hole 12a, an oil inlet hole 11b and an oil outlet hole 11 c. The shaft hole 12a, the oil inlet hole 11b and the oil outlet hole 11c communicate the pressure chamber 11a with the outer surface of the pressure block 10.
Wherein the shaft hole 12a is located at one end of the pressure chamber 11a, and the axis of the shaft hole 12a is parallel to the axis of the pressure chamber 11 a. The cross section of the shaft hole 12a is smaller than that of the pressure chamber 11 a.
The pressure shaft 20 is inserted into the shaft hole 12a, and a first end of the pressure shaft 20 is exposed outside the pressure receiving block 10. A first end of the pressure shaft 20 is provided with a coupling 22. A second end of the pressure shaft 20 is located within the pressure chamber 11 a. The second end of the pressure shaft 20 is provided with an outer flange 21 extending radially outward of the pressure shaft 20, and the outer peripheral wall of the outer flange 21 is slidably sealed with the inner wall of the pressure chamber 11 a.
The oil inlet hole 11b and the shaft hole 12a are respectively located on opposite sides of the outer flange 21, and the oil inlet hole 11b and the oil outlet hole 11c are located on the same side of the outer flange 21. The hydraulic loading system 30 communicates with the oil inlet hole 11b and the oil outlet hole 11 c. The hydraulic loading system 30 is configured to controllably pressurize the pressure chamber 11a and to make the pressure of the pressure chamber 11a constant.
According to the embodiment of the invention, the pressure cavity is arranged in the pressure bearing block, and the oil inlet and the oil outlet are arranged on the pressure bearing block, so that the pressure cavity can be pressurized by the hydraulic loading system. Through set up the shaft hole on the bearing block, with pressure shaft cartridge to the shaft hole in, because the epaxial outward flange that is provided with of pressure, the outer flange slides with the inner wall of pressure chamber and seals, the cross section in shaft hole is less than the cross section of pressure chamber, inlet port and shaft hole are located the opposite both sides of outward flange respectively, inlet port and oil outlet are located the homonymy of outward flange, consequently, after pressurizeing the pressure chamber, the outward flange can compress tightly on the inner wall of pressure chamber, and the pressure in the pressure chamber is big more, the packing force that the outward flange used on the inner wall of pressure chamber. Friction is generated between the outer flange and the inner wall of the pressure chamber, and the magnitude of the friction can be adjusted by varying the magnitude of the pressing force of the outer flange against the inner wall of the pressure chamber. When the grinding is carried out, the pressure shaft can be connected with an output shaft of equipment to be ground through a coupler on the pressure shaft, the friction force between the outer flange and the inner wall of the pressure cavity is equivalent to the load acting on the output shaft of the equipment to be ground, the size of the load can be changed by changing the size of the friction force, the working condition during grinding is the same as the working condition during actual use, therefore, the grinding effect is improved, and the grinding time is shortened.
As shown in fig. 1, the bearing block 10 may include a block-shaped body 11 and a stopper 12 detachably coupled. The stop 12 is located at one end of the pressure chamber 11a, an orthographic projection of the pressure chamber 11a on the stop 12 is located in an end face of the stop 12 close to the pressure chamber 11a, and the shaft hole 12a is located on the stop 12. By providing the pressure bearing block 10 in two parts that can be disassembled, the assembly of the pressure shaft 20 can be facilitated.
Alternatively, the stopper 12 may be screwed with the block body 11. The threaded connection has good sealing performance and convenient disassembly and assembly.
Further, a sealing ring 40 may be disposed between the block body 11 and the stopper 12. The sealing performance between the stopper 12 and the block body 11 is further improved by the seal ring 40, and leakage is reduced. The outer diameter of the sealing ring 40 can be 2-2000 mm, the sealing ring can bear high pressure, and good sealing performance can be still provided when the pressure reaches 45MPa and the linear speed of the edge of the outer flange 21 reaches 15 m/s.
A gap may be provided between the pressure shaft 20 and the shaft hole 12a so as to facilitate the discharge of air between the outer flange 21 and the stopper 12.
Fig. 2 is a schematic diagram of a hydraulic loading system according to an embodiment of the present invention. As shown in fig. 2, the hydraulic loading system 30 may include a tank 31, a loading pump 32, a check valve 33, a pressure gauge 34, and a shutoff valve 35. An oil inlet of the loading pump 32 is communicated with the oil tank 31, an oil outlet of the loading pump 32 is communicated with an oil inlet of the check valve 33, an oil outlet of the check valve 33 is communicated with the oil inlet hole 11b, an oil outlet of the check valve 33 is further connected with a pressure gauge 34, the oil outlet hole 11c is communicated with an oil inlet of the stop valve 35, and an oil outlet of the stop valve 35 is communicated with the oil tank 31. When grinding is performed, the stop valve 35 may be closed first, the pressure chamber 11a may be pressurized by the load pump 32, the pressure in the pressure chamber 11a may be obtained by the pressure gauge 34, the load pump 32 may be closed when the pressure reaches a desired value, and the backflow of the hydraulic oil may be avoided by the check valve 33, so that the pressure in the pressure chamber 11a may be kept constant. At the end of the grinding, the shut-off valve 35 can be opened to release the pressure in the pressure chamber 11 a.
Optionally, the hydraulic loading system 30 may also include a relief valve 36. An oil inlet and a pilot oil port of the overflow valve 36 are both communicated with an oil outlet of the loading pump 32, and an oil outlet of the overflow valve 36 is communicated with the oil tank 31. The pressure in the pressure chamber 11a can be adjusted to a desired level more accurately by providing the relief valve 36. Specifically, the stop valve 35 may be closed first, the opening pressure of the overflow valve 36 is set to the required pressure in the pressure chamber 11a, then the loading pump 32 is opened, the overflow valve 36 is always closed before the pressure in the pressure chamber 11a rises to the opening pressure of the overflow valve 36, and when the pressure in the pressure chamber 11a rises to the opening pressure of the overflow valve 36, the overflow valve 36 is opened, and the pressure in the pressure chamber 11a does not rise any more.
Optionally, the hydraulic loading system 30 may further comprise a filter 37, the filter 37 being connected between the oil outlet of the loading pump 32 and the oil inlet of the one-way valve 33. The filter 37 can filter the hydraulic oil, so as to prevent impurities in the hydraulic oil from damaging the hydraulic loading system 30.
Optionally, an air filter 37 may be further disposed on the oil tank 31. When the hydraulic oil is added into the oil tank 31, the hydraulic oil can be added through the air filter 37, and the air filter 37 can filter out impurities in the hydraulic oil and air, so that the hydraulic loading system 30 is prevented from being damaged by the impurities.
Optionally, a liquid level gauge 38 may be provided within the tank 31. The remaining amount of oil in the oil tank 31 is detected by the level gauge 38, ensuring that there is sufficient hydraulic oil in the oil tank 31 for use.
Optionally, an oil drain valve 311 may be further provided on the oil tank 31. When the load varying tool is not used for a long time, the hydraulic oil in the oil tank 31 can be discharged through the oil discharge valve 311.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. The variable load tool is characterized by comprising a pressure bearing block (10), a pressure shaft (20) and a hydraulic loading system (30), wherein a cylindrical pressure cavity (11a) is arranged in the pressure bearing block (10), the pressure bearing block (10) is further provided with a shaft hole (12a), an oil inlet hole (11b) and an oil outlet hole (11c), the shaft hole (12a), the oil inlet hole (11b) and the oil outlet hole (11c) are communicated with the pressure cavity (11a) and the outer surface of the pressure bearing block (10), the shaft hole (12a) is located at one end of the pressure cavity (11a), the axis of the shaft hole (12a) is parallel to the axis of the pressure cavity (11a), the cross section of the shaft hole (12a) is smaller than that of the pressure cavity (11a), the pressure shaft (20) is inserted into the shaft hole (12a), and the first end of the pressure shaft (20) is exposed out of the pressure bearing block (10), a coupling (22) is arranged at the first end of the pressure shaft (20), the second end of the pressure shaft (20) is positioned in the pressure cavity (11a), the second end of the pressure shaft (20) is provided with an outer flange (21) extending outwards along the radial direction of the pressure shaft (20), the peripheral wall of the outer flange (21) is in sliding sealing with the inner wall of the pressure chamber (11a), the oil inlet hole (11b) and the shaft hole (12a) are respectively positioned at two opposite sides of the outer flange (21), the oil inlet hole (11b) and the oil outlet hole (11c) are positioned on the same side of the outer flange (21), the hydraulic loading system (30) is communicated with the oil inlet hole (11b) and the oil outlet hole (11c), the hydraulic loading system (30) is configured to controllably pressurize the pressure chamber (11a) and to make the pressure of the pressure chamber (11a) constant.
2. The variable load tool according to claim 1, wherein the pressure bearing block (10) comprises a block body (11) and a stop block (12) which are detachably connected, the stop block (12) is located at one end of the pressure cavity (11a), an orthographic projection of the pressure cavity (11a) on the stop block (12) is located in an end face, close to the pressure cavity (11a), of the stop block (12), and the shaft hole (12a) is located on the stop block (12).
3. The variable load tooling as claimed in claim 2, wherein a sealing ring (40) is arranged between the block-shaped body (11) and the stop block (12).
4. The variable load tooling as claimed in claim 2, wherein the stop block (12) is in threaded connection with the block-shaped body (11).
5. The variable load tool according to any one of claims 1 to 4, wherein the hydraulic loading system (30) comprises an oil tank (31), a loading pump (32), a one-way valve (33), a pressure gauge (34) and a stop valve (35), an oil inlet of the loading pump (32) is communicated with the oil tank (31), an oil outlet of the loading pump (32) is communicated with an oil inlet of the one-way valve (33), an oil outlet of the one-way valve (33) is communicated with the oil inlet hole (11b), the oil outlet of the one-way valve (33) is further connected with the pressure gauge (34), the oil outlet hole (11c) is communicated with the oil inlet of the stop valve (35), and an oil outlet of the stop valve (35) is communicated with the oil tank (31).
6. The variable load tool according to claim 5, wherein the hydraulic loading system (30) further comprises an overflow valve (36), an oil inlet and a pilot oil port of the overflow valve (36) are both communicated with an oil outlet of the loading pump (32), and an oil outlet of the overflow valve (36) is communicated with the oil tank (31).
7. The variable load tooling of claim 5, wherein the hydraulic loading system (30) further comprises a filter (37), the filter (37) being connected between an oil outlet of the loading pump (32) and an oil inlet of the check valve (33).
8. The variable load tooling as claimed in claim 5, wherein a liquid level meter (38) is arranged in the oil tank (31).
9. The variable load frock of claim 5, characterized in that, be equipped with air cleaner (37) on the oil tank (31).
10. The variable load frock of claim 5, characterized in that, be equipped with oil drain valve (311) on the oil tank (31).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810986441.1A CN109114051B (en) | 2018-08-28 | 2018-08-28 | Variable load tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810986441.1A CN109114051B (en) | 2018-08-28 | 2018-08-28 | Variable load tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109114051A CN109114051A (en) | 2019-01-01 |
| CN109114051B true CN109114051B (en) | 2019-12-31 |
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ID=64860281
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810986441.1A Active CN109114051B (en) | 2018-08-28 | 2018-08-28 | Variable load tool |
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| Country | Link |
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| CN (1) | CN109114051B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110426188B (en) * | 2019-06-28 | 2021-06-01 | 武汉船用机械有限责任公司 | Load testing tool |
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| CN104093993A (en) * | 2012-01-31 | 2014-10-08 | 伊顿公司 | System and method for maintaining constant loads in hydraulic systems |
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| WO2015174250A1 (en) * | 2014-05-15 | 2015-11-19 | カヤバ工業株式会社 | Fluidic control device |
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| CN105697353B (en) * | 2016-01-21 | 2017-11-24 | 燕山大学 | A kind of variable working condition Hydraulic pump fault simulation and state-detection combined test apparatus |
| CN107917118A (en) * | 2016-10-10 | 2018-04-17 | 罗伯特·博世有限公司 | Composite control hydraulic circuit |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9458818B2 (en) * | 2014-07-22 | 2016-10-04 | Caterpillar Global Mining Llc | Hydraulic system for machine |
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2018
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103109095A (en) * | 2010-03-17 | 2013-05-15 | 派克汉尼芬公司 | Hydraulic valve with pressure limiter |
| CN101967980A (en) * | 2010-05-17 | 2011-02-09 | 浙江大学 | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control |
| CN101967980B (en) * | 2010-05-17 | 2012-12-12 | 浙江大学 | Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control |
| CN104093993A (en) * | 2012-01-31 | 2014-10-08 | 伊顿公司 | System and method for maintaining constant loads in hydraulic systems |
| CN104763693A (en) * | 2014-01-02 | 2015-07-08 | 卡特彼勒路面机械公司 | Torque limit control |
| WO2015174250A1 (en) * | 2014-05-15 | 2015-11-19 | カヤバ工業株式会社 | Fluidic control device |
| CN106536944A (en) * | 2014-06-18 | 2017-03-22 | 凯斯纽荷兰(中国)管理有限公司 | A safety hydraulic circuit |
| CN105697353B (en) * | 2016-01-21 | 2017-11-24 | 燕山大学 | A kind of variable working condition Hydraulic pump fault simulation and state-detection combined test apparatus |
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| CN107917118A (en) * | 2016-10-10 | 2018-04-17 | 罗伯特·博世有限公司 | Composite control hydraulic circuit |
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| Publication number | Publication date |
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| CN109114051A (en) | 2019-01-01 |
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