CN111175000A - Dual cooling system suitable for large-displacement electro-hydraulic servo actuator - Google Patents
Dual cooling system suitable for large-displacement electro-hydraulic servo actuator Download PDFInfo
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- CN111175000A CN111175000A CN202010175981.9A CN202010175981A CN111175000A CN 111175000 A CN111175000 A CN 111175000A CN 202010175981 A CN202010175981 A CN 202010175981A CN 111175000 A CN111175000 A CN 111175000A
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- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
- G01M7/022—Vibration control arrangements, e.g. for generating random vibrations
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
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Abstract
The invention discloses a double cooling system suitable for a large-displacement electro-hydraulic servo actuator, which is used for the electro-hydraulic servo actuator, wherein the electro-hydraulic servo actuator is connected with an oil inlet and an oil return port, and the oil return port is directly connected with a large-flow pump station oil tank through an oil pipe; the cold oil pump is connected with a motor through a coupler, and an oil outlet of the cold oil pump is respectively connected with an oil inlet of the oil-cold pressure limiting valve, the oil temperature and oil pressure integrated sensor and an oil inlet of the evaporator through oil pipes; and a refrigerant inlet of the evaporator is respectively connected with an outlet of the dryer and an inlet of the electromagnetic stop valve, and a refrigerant outlet of the evaporator is respectively connected with a low-pressure port of the pressure limiting valve, a liquid return port of the liquid storage tank and an oil return port of the electro-hydraulic servo actuator. The invention realizes double cooling of working medium and environment of the electro-hydraulic servo actuator, improves the cooling effect of the working engineering of the electro-hydraulic servo actuator, and greatly reduces the noise generated by a cooling system; the cooling efficiency is improved, the pipeline corrosion is avoided, and the energy consumption of the system is reduced.
Description
Technical Field
The invention relates to the technical field of large-displacement electro-hydraulic servo actuators, in particular to a dual cooling system suitable for the large-displacement electro-hydraulic servo actuator.
Background
The large-displacement electro-hydraulic servo actuator is important equipment for road vibration simulation and fatigue analysis tests of heavy-duty vehicles in the field of national defense, and is an important test equipment guarantee for the design of a traveling system and key parts of the national defense heavy-duty vehicles. The piston and the cylinder body of the large-displacement electro-hydraulic servo actuator perform reciprocating high-frequency friction and the working fluid performs repeated high-frequency switching on pressure loss to generate heat, the temperature is finally increased, working characteristic changes and structural micro deformation of the working fluid are caused, the distortion degree of electro-hydraulic servo control is increased, vibration simulation precision of the large-displacement electro-hydraulic servo actuator is reduced, and even part of the structure is damaged. The good cooling system is a protective umbrella which reduces the control difficulty of the electro-hydraulic servo actuator, reduces the distortion degree of the electro-hydraulic servo control, and improves the vibration simulation precision of the large-displacement electro-hydraulic servo actuator and the service life of the actuator.
The Chinese patent with application number '201711128312.0' discloses a radiator oil return control system of an oil cylinder and a control method thereof, wherein a main loop is directly connected in series with a water-cooling cooler, and the flow of hydraulic oil entering the water-cooling cooler is controlled by a control valve to carry out oil liquid heat dissipation and cooler protection. The method increases the working back pressure of the main loop, can influence the electro-hydraulic servo control of the electro-hydraulic servo actuator, and simultaneously, the working medium water easily causes pipeline corrosion. Distilled water is often used to avoid this phenomenon, which greatly increases the cost.
The heat source generated in the working process of the large-displacement electro-hydraulic servo actuator is the reciprocating high-frequency friction of the piston and the cylinder body and the repeated high-frequency switching pressure loss of working fluid. In order to ensure the working performance of the electro-hydraulic servo actuator, the wall thickness of the cylinder body designed by rigidity is thicker, and the temperature of the reciprocating motion position of the cylinder body and the piston is higher only by radiating through the wall surface of the cylinder body, which is also the reason that the wall surface of the common vibration exciter is scalded when the common vibration exciter works for a period of time.
The Chinese patent with the application number of 201910408163.6 provides a self-radiating type quick multi-cavity hydraulic oil cylinder, which is connected with a fixing ring and a fixing block by arranging a plurality of clamping grooves on the outer walls of two sides of a cylinder body, forms a plurality of radiating cavities with a shell, increases the radiating area of the cylinder body, and radiates heat through water cooling or air cooling. The method starts from only processing the ambient temperature, and cannot avoid the influence of the temperature on the working fluid and seriously influence the electro-hydraulic servo control precision. In addition, the cylinder body heat dissipation cavity is complex in composition and large in occupied space.
In summary, the main problems in the prior art include: the working fluid of the large-displacement electro-hydraulic servo actuator is more in heat generated by repeated high-frequency switching pressure loss, the piston and the cylinder body are larger in heat generated by reciprocating high-frequency friction and the cylinder body is insufficient in heat dissipation, and higher requirements are provided for the cooling performance of a cooling system of the large-displacement electro-hydraulic servo actuator, such as maintaining working medium and environment temperature, improving cooling efficiency, avoiding pipeline corrosion, reducing cooling energy consumption and noise and the like. The prior art fails to meet the above requirements.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a double cooling system suitable for a large-displacement electro-hydraulic servo actuator, which realizes double cooling of working media and environment of the electro-hydraulic servo actuator, improves the cooling effect of the work engineering of the electro-hydraulic servo actuator, and greatly reduces the noise generated by the cooling system; the cooling efficiency is improved, the pipeline corrosion is avoided, and the energy consumption of the system is reduced.
Therefore, the invention adopts the following technical scheme:
a double cooling system suitable for a large-displacement electro-hydraulic servo actuator is used for the electro-hydraulic servo actuator, an oil inlet and an oil return port are connected to the electro-hydraulic servo actuator, and the oil return port is directly connected with a large-flow pump station oil tank through an oil pipe; the oil tank of the large-flow pump station is respectively connected with an oil suction port of the cold oil pump, an oil return port of the oil-cooling pressure limiting valve and an oil return port of the filter; the cold oil pump is connected with a motor through a coupler, and an oil outlet of the cold oil pump is respectively connected with an oil inlet of the oil-cold pressure limiting valve, the oil temperature and oil pressure integrated sensor and an oil inlet of the evaporator through oil pipes; a refrigerant inlet of the evaporator is respectively connected with an outlet of the dryer and an inlet of the electromagnetic stop valve, and an outlet of the electromagnetic stop valve is connected with a cooling medium inlet and an inner cavity temperature sensor on the electro-hydraulic servo actuator; the oil outlet of the evaporator is connected with the inlet of the filter; a refrigerant outlet of the evaporator is respectively connected with a low-pressure port of the pressure limiting valve, a liquid return port of the liquid storage tank and an oil return port of the electro-hydraulic servo actuator; the high-pressure port of the pressure limiting valve is connected with the outlet of the compressor; the inlet of the compressor is connected with the outlet of the liquid storage tank, and the outlet of the compressor is also connected with the refrigerant inlet of the condenser; the water-cooling inlet of the condenser is connected with the outlet below the cooling water tower through a cooling water pipe, and the inlet above the cooling water tower is connected with the water-cooling outlet of the condenser; the refrigerant outlet of the condenser is connected with the inlet of the expansion valve, and the outlet of the expansion valve is connected with the inlet of the dryer.
Preferably, a pressure relay is arranged in the liquid storage tank and used for monitoring the pressure of the liquid storage tank.
Preferably, the electro-hydraulic servo actuator comprises an integrated piston rod, an upper end cover, an upper flow distribution sealing gasket, a cylinder body, a transition valve block, an electro-hydraulic servo valve, a lower end cover, a lower flow distribution sealing gasket and a base; the integrated piston rod is positioned inside the cylinder body, and the upper end cover and the lower end cover are respectively positioned at two ends of the cylinder body; the upper flow distribution sealing gasket is positioned between the upper end cover and the cylinder body and used for sealing; the lower flow distribution sealing gasket is positioned between the lower end cover and the cylinder body and used for sealing; the transition valve block and the electro-hydraulic servo valve are positioned on one side of the cylinder body and used for controlling hydraulic oil to enter the cylinder body.
Preferably, the cylinder body comprises a cooling hole, a distributing groove, an outlet welding joint, an inlet welding interface, an end cover connecting hole, a first oil inlet and a second oil inlet; the end cover connecting holes are uniformly arranged in the cylinder body in n numbers and are used for realizing the fixation of an end cover and the compaction of a flow distribution sealing gasket; n cooling holes are arranged between two adjacent end cover connecting holes; two cooling holes and adjacent holes are not provided with distribution grooves, and the rest cooling holes are continuously arranged after being provided with distribution grooves and separated by one cooling hole; n is an even number.
Preferably, the upper distributing sealing gasket comprises an upper cold hole, an upper distributing groove and an upper connecting hole; the upper connecting holes are uniformly provided with n upper flow distribution sealing gaskets and are used for realizing the fixation of an upper end cover and the compaction of the upper flow distribution sealing gaskets; n upper cold holes are arranged between every two adjacent upper connecting holes; two upper cold holes and the adjacent holes are not provided with upper distributing grooves, and the other upper cold holes are provided with upper distributing grooves and then are continuously configured after being separated by one upper cold hole; n is an even number.
Preferably, the lower distributing sealing gasket comprises a lower cold hole, a lower distributing groove, a lower connecting hole and a base connecting hole; the lower connecting holes are uniformly arranged in n numbers on the lower flow distribution sealing gasket and are used for realizing the fixation of the lower end cover and the compaction of the lower flow distribution sealing gasket; n lower cooling holes are arranged between every two adjacent lower connecting holes; a lower distributing groove is continuously arranged on the lower distributing sealing gasket at intervals between the adjacent lower cooling holes; n is an even number.
Preferably, the electro-hydraulic servo actuator is further provided with a cooling medium outlet.
Preferably, the refrigerant used in the evaporator is CO2。
Preferably, the oil temperature and oil pressure integrated sensor is used for realizing energy-saving control of the cooling system, and when the measured pressure is less than a set pressure value or the oil temperature is lower than a set temperature, the judgment is made that cooling is not needed, and the compressor does not act; the set pressure value is 0.5-1Mpa, and the set temperature is 30-35 ℃.
Preferably, the inner cavity temperature sensor and the electromagnetic stop valve are used for realizing energy-saving control of the environmental temperature of the inner cavity of the electro-hydraulic servo actuator, and when the temperature detected by the inner cavity temperature sensor is lower than a set temperature value, the electromagnetic stop valve is closed; the set temperature value is 35-40 ℃.
Compared with the prior art, the invention has the beneficial effects that:
(1) the double cooling of the working medium and the environment of the electro-hydraulic servo actuator is realized, the cooling effect of the operation engineering of the electro-hydraulic servo actuator is improved, and the noise generated by a cooling system is greatly reduced.
(2) The refrigeration system is arranged on a hydraulic control system bypass and a cylinder body, is decoupled with the main hydraulic control loop, and has no adverse effect on the response and control precision of the electro-hydraulic servo actuator.
(3) Working medium and refrigerant CO of electrohydraulic servo actuator2The evaporator directly carries out heat exchange, the temperature difference between the two media is large, and the heat exchange efficiency is higher.
(4) The cylinder body is provided with a pipeline, flow distribution grooves are formed in two ends of the cylinder body, and an open S-shaped capillary heat dissipation channel is constructed by combining a flow distribution sealing gasket and an end cover on the basis of keeping the main structure of the electro-hydraulic servo actuator, so that a better working environment is provided for the actuator.
(5) Refrigerant CO2The heat exchange is carried out between the evaporator and the heat dissipation channel of the capillary tube, so that the actuator cylinder body and the tube are less corroded, and the service life is longer.
(6) The oil temperature, the oil pressure and the cylinder body temperature are subjected to three-parameter feedback control, and the energy consumption of a cooling system is low.
Drawings
Fig. 1 is a schematic structural composition and working principle diagram of a dual cooling system adapted to a large displacement electro-hydraulic servo actuator according to an embodiment of the present invention.
3 FIG. 32 3 is 3 a 3 cross 3- 3 sectional 3 view 3 A 3- 3 A 3 of 3 an 3 electro 3- 3 hydraulic 3 servo 3 actuator 3 provided 3 in 3 accordance 3 with 3 an 3 embodiment 3 of 3 the 3 present 3 invention 3. 3
FIG. 3 is a top view of a cylinder of an electro-hydraulic servo actuator provided by an embodiment of the present invention.
FIG. 4 is a cross-sectional view B-B of a cylinder of an electro-hydraulic servo actuator provided by an embodiment of the present invention.
Fig. 5 is a schematic structural diagram of an upper flow distribution gasket according to an embodiment of the present invention.
Fig. 6 is a schematic structural view of a lower distribution gasket according to an embodiment of the present invention.
Description of reference numerals: 1. an electro-hydraulic servo actuator; 2. a coolant inlet; 3. an inner cavity temperature sensor; 4. an electromagnetic cut-off valve; 5. an evaporator; 6. a dryer; 7. an expansion valve; 8. a condenser; 9. a cooling water tower; 10. a cooling water pipe; 11. a pressure limiting valve; 12. a compressor; 13. a liquid storage tank; 14. a pressure relay; 15. a large-flow pump station oil tank; 16. an oil-cooled pressure limiting valve; 17. an electric motor; 18. a coupling; 19. a cold oil pump; 20. an oil temperature and oil pressure integrated sensor; 21. a filter; 22. an oil inlet; 23. an oil return port; 24. a coolant outlet; 101. an integrated piston rod; 102. an upper end cover; 103. an upper flow distribution gasket; 104. a cylinder body; 105. a transition valve block; 106. an electro-hydraulic servo valve; 107. a lower end cover; 108. a lower flow distributing gasket; 109. a base; 1041. a cooling hole; 1042. a distributing groove; 1043. an outlet weld joint; 1044. an inlet welding interface; 1045. an end cap connection hole; 1046. a first oil inlet; 1047. a second oil inlet; 1031. an upper cold hole; 1032. an upper distributing groove; 1033. an upper connecting hole; 1081. a lower cooling hole; 1082. a lower distribution groove; 1083. a lower connecting hole; 1084. the base is connected with the hole.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings and specific embodiments, which are provided for illustration only and are not to be construed as limiting the invention.
Examples
As shown in FIG. 1, the invention discloses a double cooling system for a large-displacement electro-hydraulic servo actuator, which is used for the electro-hydraulic servo actuator 1; an oil inlet 22 and an oil return port 23 are connected to the electro-hydraulic servo actuator 1, and the oil return port 23 is directly connected with the large-flow pump station oil tank 15 through an oil pipe; the oil tank 15 of the large-flow pump station is respectively connected with an oil suction port of a cold oil pump 19, an oil return port of an oil-cooling pressure-limiting valve 16 and an oil return port of a filter 21. The cold oil pump 19 is connected with the motor 17 through the coupler 18, and an oil outlet of the cold oil pump 19 is respectively connected with an oil inlet of the oil cold pressure limiting valve 16, the oil temperature and oil pressure integrated sensor 20 and an oil inlet of the evaporator 5 through oil pipes. The refrigerant inlet of the evaporator 5 is connected with the outlet of the dryer 6 and the inlet of the electromagnetic stop valve 4, and the outlet of the electromagnetic stop valve 4 is connected with the cooling medium inlet 2 and the inner cavity temperature sensor 3 on the electro-hydraulic actuator 1. The oil outlet of the evaporator 5 is connected with the inlet of the filter 21. The refrigerant outlet of the evaporator 5 is respectively connected with the low-pressure port of the pressure limiting valve 11, the liquid return port of the liquid storage tank 13 and the oil return port 23 of the electro-hydraulic servo actuator 1. The high-pressure port of the pressure limiting valve 11 is connected with the outlet of the compressor 12. The inlet of the compressor 12 is connected with the outlet of a liquid storage tank 13, and a pressure relay 14 is arranged in the liquid storage tank 13. The outlet of the compressor 12 is also connected to the refrigerant inlet of the condenser 8. The water-cooling inlet of the condenser 8 is connected with the outlet below the cooling water tower 9 through a cooling water pipe 10, and the inlet above the cooling water tower 9 is connected with the water-cooling outlet of the condenser 8. The refrigerant outlet of the condenser 8 is connected to the inlet of the expansion valve 7, and the outlet of the expansion valve 7 is connected to the inlet of the dryer 6.
As shown in fig. 2, the electro-hydraulic servo actuator 1 includes an integrated piston rod 101, an upper end cap 102, an upper distribution seal 103, a cylinder 104, a transition valve block 105, an electro-hydraulic servo valve 106, a lower end cap 107, a lower distribution seal 108, and a base 109.
As shown in fig. 3 and 4, the cylinder block 104 includes a cooling hole 1041, a flow distribution groove 1042, an outlet weld joint 1043, an inlet weld interface 1044, an end cover connection hole 1045, a first oil inlet 1046, and a second oil inlet 1047. The end cover connecting holes 1045 are uniformly provided with n (n is an even number) on the cylinder body, so that the end cover is fixed and the flow distribution gasket is compressed. Cooling holes 1041 (n in total) are arranged between two adjacent end cover connecting holes 1045, wherein the flow distribution grooves 1042 are not arranged in two cooling holes 1041 and the adjacent holes, and the rest of the cooling holes 1041 are arranged in a continuous manner after being provided with the flow distribution grooves 1042 and spaced by one cooling hole 1041.
As shown in fig. 5, the upper distribution gasket 103 includes an upper cold hole 1031, an upper distribution groove 1032, and an upper connection hole 1033. The upper connecting holes 1033 are uniformly arranged on the upper flow distribution sealing gasket 103 in n numbers (n is an even number), so that the upper end cover 102 is fixed and the upper flow distribution sealing gasket 103 is pressed tightly. Upper cold holes 1031 (n in total) are arranged between two adjacent upper connecting holes 1033, wherein the upper flow distribution grooves 1032 are not arranged in two upper cold holes 1031 and the adjacent holes, and the other upper cold holes 1031 are arranged after the upper flow distribution grooves 1032 are arranged and are continuously arranged after one upper cold hole 1031 is separated.
As shown in FIG. 6, the lower distribution gasket 108 includes a lower cold hole 1081, a lower distribution groove 1082, a lower tie hole 1083 and a base tie hole 1084. The lower connecting holes 1083 are uniformly arranged in number n (n is an even number) on the lower flow distribution sealing gasket, so that the fixation of the lower end cover 107 and the compression of the lower flow distribution sealing gasket 108 are realized. And a lower cooling hole 1081 (n in total) is arranged between two adjacent lower connecting holes 1083. The lower distribution grooves 1082 are provided in the lower distribution packing 108 so as to be continuously spaced from the adjacent lower cooling holes 1081.
The working principle of the double cooling system adapting to the large-displacement electro-hydraulic servo actuator is as follows: hydraulic oil enters a transition valve block 105 of the electro-hydraulic servo actuator 1 from an oil inlet 22, and is controlled to enter a first oil inlet 1046 (or a second oil inlet 1047) of a cylinder body 104 through an electro-hydraulic servo valve 106, so that the integrated piston rod 101 is pushed to repeatedly move; the hydraulic oil directly returns to the large-flow pump station oil tank 15 from the oil return port 23 through the electro-hydraulic servo valve 106 and the transition valve block 105 from the second oil inlet 1047 (or the first oil inlet 1046) of the cylinder body. The cold oil pump 19 sucks oil from the oil tank 15 of the large-flow pump station, the discharged hydraulic oil enters the oil inlet of the evaporator 5 and is mixed with refrigerant CO in the evaporator 52After the heat exchange is finished, the working medium flows back to the large-flow pump station oil tank 15 from the oil outlet of the evaporator 5 through the filter 21, and the heat dissipation of the working medium is finished. The oil-cooled pressure-limiting valve 16 is used for pressure protection of the cooling circuit. The oil temperature and oil pressure integrated sensor 20 is used for realizing energy-saving control of the cooling system, and when the measured pressure is less than a set value (generally 0.5-1Mpa) or the oil temperature is lower than 30-35 ℃, the compressor 12 does not act and the cooling is not needed.
Refrigerant CO in evaporator 52The refrigerant CO in the liquid storage tank 13 is sucked by the compressor 122Then the mixture is sent into the condenser 8, the expansion valve 7 and the dryer 6. Refrigerant CO in condenser 82The heat exchange is completed through the water extracted by the cooling water tower 9, and the high pressure and the high temperature are changed into the high pressure and the medium temperature state. A pressure limiting valve 11 is provided at the outlet of the compressor 12 to control the refrigerant circuit pressure. The pressure relay 14 monitors the pressure of the liquid storage tank 13, and when the pressure is less than a set value (0.5-0.55Mpa), an alarm is given to prompt the addition of the refrigerant.
Part of the refrigerant at the outlet of the dryer 6 enters the cylinder 104 through the electromagnetic stop valve 4 and the cooling medium inlet 2 on the electro-hydraulic servo actuator 1. Cooling hole 1041, flow distribution groove 1042, outlet welding joint 1043, inlet welding interface 1044 and end cover connecting hole 10 in cylinder body 10445. The first inlet 1046 and the second inlet 1047 form a long open S-shaped capillary radiating pipe. The refrigerant flows through the S-shaped radiating pipe to take away the ambient heat around the cylinder body 104, flows out of the electro-hydraulic servo actuator 1 through the outlet welding joint 1043, and enters the back buckle of the liquid storage tank 13. CO 22Compared with water and air, the cylinder has long service life, controllable temperature of refrigerant and higher cooling efficiency under larger temperature difference. The inner cavity temperature sensor 3 and the electromagnetic stop valve 4 are used for realizing energy-saving control of the environment temperature of the cylinder body 104, and when the temperature detected by the inner cavity temperature sensor 3 is less than a set value (35-40 ℃), the electromagnetic stop valve 4 is closed.
The cooling system configured by the same electro-hydraulic servo actuator has lower power and greatly reduces the noise of the cooling system with high efficiency.
The above description is only exemplary of the present invention and should not be taken as limiting the invention, as any modification, equivalent replacement, or improvement made within the spirit and scope of the present invention should be included in the present invention.
Claims (10)
1. The utility model provides a dual cooling system who adapts to big displacement electro-hydraulic servo actuator which characterized in that: the dual cooling system is used for an electro-hydraulic servo actuator (1), an oil inlet (22) and an oil return port (23) are connected to the electro-hydraulic servo actuator (1), and the oil return port (23) is directly connected with a large-flow pump station oil tank (15) through an oil pipe; the oil tank (15) of the large-flow pump station is respectively connected with an oil suction port of a cold oil pump (19), an oil return port of an oil-cold pressure limiting valve (16) and an oil return port of a filter (21); the cold oil pump (19) is connected with a motor (17) through a coupler (18), and an oil outlet of the cold oil pump (19) is respectively connected with an oil inlet of an oil-cold pressure limiting valve (16), an oil temperature and oil pressure integrated sensor (20) and an oil inlet of the evaporator (5) through oil pipes; a refrigerant inlet of the evaporator (5) is respectively connected with an outlet of the dryer (6) and an inlet of the electromagnetic stop valve (4), and an outlet of the electromagnetic stop valve (4) is connected with a cooling medium inlet (2) and an inner cavity temperature sensor (3) on the electro-hydraulic servo actuator (1); the oil outlet of the evaporator (5) is connected with the inlet of the filter (21); a refrigerant outlet of the evaporator (5) is respectively connected with a low-pressure port of the pressure limiting valve (11), a liquid return port of the liquid storage tank (13) and an oil return port (23) of the electro-hydraulic servo actuator (1); the high-pressure port of the pressure limiting valve (11) is connected with the outlet of the compressor (12); the inlet of the compressor (12) is connected with the outlet of the liquid storage tank (13), and the outlet of the compressor (12) is also connected with the refrigerant inlet of the condenser (8); a water-cooling inlet of the condenser (8) is connected with an outlet below the cooling water tower (9) through a cooling water pipe (10), and an inlet above the cooling water tower (9) is connected with a water-cooling outlet of the condenser (8); the refrigerant outlet of the condenser (8) is connected with the inlet of the expansion valve (7), and the outlet of the expansion valve (7) is connected with the inlet of the dryer (6).
2. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 1, wherein: and a pressure relay (14) is arranged in the liquid storage tank (13), and the pressure relay (14) is used for monitoring the pressure of the liquid storage tank (13).
3. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 1, wherein: the electro-hydraulic servo actuator (1) comprises an integrated piston rod (101), an upper end cover (102), an upper flow distribution sealing gasket (103), a cylinder body (104), a transition valve block (105), an electro-hydraulic servo valve (106), a lower end cover (107), a lower flow distribution sealing gasket (108) and a base (109); the integrated piston rod (101) is positioned inside the cylinder body (104), and the upper end cover (102) and the lower end cover (107) are respectively positioned at two ends of the cylinder body (104); the upper flow distribution sealing gasket (103) is positioned between the upper end cover (102) and the cylinder body (104) and is used for sealing; the lower flow distribution sealing gasket (108) is positioned between the lower end cover (107) and the cylinder body (104) and used for sealing; the transition valve block (105) and the electro-hydraulic servo valve (106) are positioned on one side of the cylinder body (104) and used for controlling hydraulic oil to enter the cylinder body (104).
4. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 3, wherein: the cylinder block (104) comprises a cooling hole (1041), a flow distribution groove (1042), an outlet welding joint (1043), an inlet welding joint (1044), an end cover connecting hole (1045), a first oil inlet (1046) and a second oil inlet (1047); the end cover connecting holes (1045) are uniformly arranged in n numbers on the cylinder body (104) and are used for realizing the fixation of an end cover and the compaction of a flow distribution sealing gasket; cooling holes (1041) are arranged between two adjacent end cover connecting holes (1045), and the number of the cooling holes is n; two of the cooling holes (1041) and the adjacent holes are not provided with the distribution grooves (1042), and the rest of the cooling holes (1041) are arranged with the distribution grooves (1042) and then are continuously arranged with a space between the cooling holes (1041); n is an even number.
5. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 3, wherein: the upper flow distribution sealing gasket (103) comprises an upper cold hole (1031), an upper flow distribution groove (1032) and an upper connecting hole (1033); the upper connecting holes (1033) are uniformly arranged on the upper flow distribution sealing gasket (103) in n numbers and are used for realizing the fixation of the upper end cover (102) and the compaction of the upper flow distribution sealing gasket (103); n upper cold holes (1031) are arranged between two adjacent upper connecting holes (1033); two upper cold holes (1031) and the adjacent holes are not provided with the upper distributing grooves (1032), and the other upper cold holes (1031) are arranged on the upper distributing grooves (1032) and are continuously arranged after being separated by one upper cold hole (1031); n is an even number.
6. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 3, wherein: the lower distributing sealing gasket (108) comprises a lower cooling hole (1081), a lower distributing groove (1082), a lower connecting hole (1083) and a base connecting hole (1084); n lower connecting holes (1083) are uniformly formed in the lower flow distribution sealing gasket (108) and used for fixing the lower end cover (107) and pressing the lower flow distribution sealing gasket (108); n lower cooling holes (1081) are arranged between two adjacent lower connecting holes (1083); a lower distributing groove (1082) is continuously arranged on the lower distributing gasket (108) at intervals between the adjacent lower cooling holes (1081); n is an even number.
7. A dual cooling system for a large displacement electro-hydraulic servo actuator as defined in any one of claims 1 to 6, wherein: and a cooling medium outlet (24) is also arranged on the electro-hydraulic servo actuator (1).
8. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 7, wherein: the refrigerant used in the evaporator (5) is CO2。
9. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 7, wherein: the oil temperature and oil pressure integrated sensor (20) is used for realizing energy-saving control of the cooling system, and when the measured pressure is less than a set pressure value or the oil temperature is lower than a set temperature, the compressor (12) does not act and is judged not to need cooling; the set pressure value is 0.5-1Mpa, and the set temperature is 30-35 ℃.
10. The dual cooling system for a large displacement electro-hydraulic servo actuator as claimed in claim 7, wherein: the inner cavity temperature sensor (3) and the electromagnetic stop valve (4) are used for realizing energy-saving control of the inner cavity environment temperature of the electro-hydraulic servo actuator (1), and when the temperature detected by the inner cavity temperature sensor (3) is less than a set temperature value, the electromagnetic stop valve (4) is closed; the set temperature value is 35-40 ℃.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010175981.9A CN111175000B (en) | 2020-03-13 | 2020-03-13 | Dual cooling system suitable for large-displacement electro-hydraulic servo actuator |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010175981.9A CN111175000B (en) | 2020-03-13 | 2020-03-13 | Dual cooling system suitable for large-displacement electro-hydraulic servo actuator |
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| CN111175000A true CN111175000A (en) | 2020-05-19 |
| CN111175000B CN111175000B (en) | 2021-08-03 |
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| CN202010175981.9A Active CN111175000B (en) | 2020-03-13 | 2020-03-13 | Dual cooling system suitable for large-displacement electro-hydraulic servo actuator |
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2955574A (en) * | 1958-01-13 | 1960-10-11 | Gen Motors Corp | Hydraulic actuator having cooling fluid circulation |
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|---|---|
| CN111175000B (en) | 2021-08-03 |
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