CN217056541U - Compact servo electro-hydraulic actuator - Google Patents
Compact servo electro-hydraulic actuator Download PDFInfo
- Publication number
- CN217056541U CN217056541U CN202122562601.XU CN202122562601U CN217056541U CN 217056541 U CN217056541 U CN 217056541U CN 202122562601 U CN202122562601 U CN 202122562601U CN 217056541 U CN217056541 U CN 217056541U
- Authority
- CN
- China
- Prior art keywords
- port
- valve
- oil inlet
- oil
- hydraulic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Abstract
The utility model provides a compact servo electro-hydraulic actuator, which comprises a hydraulic cylinder, wherein one side of the hydraulic cylinder is provided with an integrated valve group, the other side of the hydraulic cylinder is provided with a bidirectional hydraulic pump, the bidirectional hydraulic pump is in transmission connection with a servo motor, the bidirectional hydraulic pump is connected with the integrated valve group through a pump connecting pipe, and the hydraulic cylinder is connected with the integrated valve group; the compact servo electro-hydraulic actuator does not need an additional pump station, has a small and compact structure, can realize a telescopic function to meet the use requirement, and is convenient and quick to install and maintain; the integrated valve group is connected with other components for control, so that the number of pipes exposed outside is reduced, and oil leakage points are not easy to generate.
Description
Technical Field
The utility model belongs to the technical field of the executor, concretely relates to servo electric liquid executor of compact.
Background
The actuator is an actuator and control valve combination in an automatic control system.
In the prior art, as disclosed in chinese utility model patent publication No. CN210240145U, a hydraulic system and a mechanical arm of a linear electro-hydraulic actuator are disclosed. The hydraulic system comprises a bidirectional hydraulic pump, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve, the first one-way valve, the second one-way valve, an oil supplementing energy accumulator and a hydraulic cylinder, wherein a first oil port of the bidirectional hydraulic pump is communicated with an oil inlet of the first hydraulic control one-way valve; the large oil tank is not needed, and the mechanical arm is not needed to be provided with an independent hydraulic power station, so that the size of a hydraulic system of the mechanical arm is reduced.
Above-mentioned prior art, though do not need hydraulic power station, the volume is less, but does not disclose the concrete structure of electro-hydraulic actuator, if hydraulic line directly exposes outside, produce easily in the use and leak oily point, the later maintenance work load is great.
Therefore, a compact servo electro-hydraulic actuator with a small and compact structure and less possibility of generating oil leakage points needs to be designed to solve the technical problems faced at present.
SUMMERY OF THE UTILITY MODEL
To the not enough that exists among the prior art, the utility model provides a small and exquisite compactness of structure, difficult production leak the servo electro-hydraulic actuator of compact of oil point.
The technical scheme of the utility model is that: compact servo electro-hydraulic actuator, including the pneumatic cylinder, one side of pneumatic cylinder is equipped with integrated valves, the opposite side of pneumatic cylinder is equipped with two-way hydraulic pump, two-way hydraulic pump transmission is connected with servo motor, two-way hydraulic pump pass through the pump connecting pipe with integrated valves is connected, the pneumatic cylinder with integrated valves is connected.
The hydraulic cylinder is provided with a front cylinder body and a rear cylinder body, the front cylinder body is coaxially connected with the rear cylinder body, and a front piston is assembled in the front cylinder body; one side of the front piston, which is close to the rear cylinder body, is connected with a rear rod body, a rear piston is assembled on the rear rod body, and the other side of the front piston is connected with a front rod body; the rear cylinder body is internally provided with a cavity A1 which is separated by a rear piston and is close to one side of the front cylinder body, the front cylinder body is internally provided with a cavity A2 which is separated by a front piston and is close to one side of the rear cylinder body, and the cavity A3 is arranged on the other side of the front cylinder body.
The integrated valve block has: the valve group body is provided with an A port, a B port, an A1 port, an A2 port and an A3 port, the A port and the B port are connected with the bidirectional hydraulic pump through pump connecting pipes, the A1 port is connected with the A1 cavity, the A2 port is connected with the A2 cavity, and the A3 port is connected with the A3 cavity; an oil outlet of the first check valve is connected with the port A, and an oil inlet of the first check valve is connected with the port A3 through a fifth overflow valve; an oil outlet of the second one-way valve is connected with the port B, and an oil inlet of the second one-way valve is connected with an oil inlet of the first one-way valve; an oil inlet of the third one-way valve is connected with the port A2, an oil outlet of the third one-way valve is respectively connected with the port A, the port A2 and the port A3, and a sixth reversing valve is connected between the oil outlet of the third one-way valve and the port A3; an oil outlet of the fourth one-way valve is connected with the port A3, and an oil inlet of the fourth one-way valve is connected with an oil inlet of the third one-way valve; an oil inlet of the first overflow valve is connected with the port A, and an oil outlet of the first overflow valve is connected with an oil outlet of the first one-way valve; an oil inlet of the second overflow valve is connected with the port B, and an oil outlet of the second overflow valve is connected with an oil outlet of the first overflow valve; an oil inlet of the third overflow valve is connected with the port A2, and an oil outlet of the third overflow valve is connected with an oil inlet of the third one-way valve; an oil outlet of the fourth overflow valve is connected with the port A3 through a fourth reversing valve, an oil inlet of the fourth overflow valve is connected with two branches, one branch is connected with the port A1 through a pressure compensation flow control valve, and the other branch is connected with the port B through a fifth reversing valve and a third reversing valve in sequence; an oil inlet of the first reversing valve is connected with the port A2, and an oil outlet of the first reversing valve is connected with the port A; and an oil inlet of the second reversing valve is connected with the port A3, and an oil inlet is connected with the button B.
The valve group body is further provided with a filter, an oil inlet of the filter is connected with the bidirectional hydraulic pump, and an oil outlet of the filter is connected with an oil inlet of the first one-way valve.
The valve group body is provided with an energy accumulator and an SP (service provider) port connected with the energy accumulator, and the SP port is connected with an oil inlet of the first one-way valve.
The accumulator is pre-charged with air pressure.
The valve group body is provided with a first pressure sensor and an SP3 port connected with the first pressure sensor, and the SP3 port is connected with an oil inlet of the first one-way valve; the valve block body is provided with a second pressure sensor and an SP2 port connected with the second pressure sensor, and the SP2 port is connected with the A1 port; the valve block body is provided with a third pressure sensor and an SP1 port connected with the third pressure sensor, and the SP1 port is connected with the A2 port.
The first reversing valve, the second reversing valve, the third reversing valve and the fourth reversing valve are two-position three-way electromagnetic reversing valves; the fifth reversing valve is a two-position communication stop type electromagnetic reversing valve; and the sixth reversing valve is a two-position four-electromagnetic reversing valve.
And a heat dissipation module is assembled on the outer side of the integrated valve group.
The heat dissipation module is provided with a heat conduction shell in contact connection with the integrated valve group, a heat dissipation liquid channel is formed in the heat conduction shell, one side of the heat conduction shell is provided with a liquid inlet connected with one end of the heat dissipation liquid channel, and the other side of the heat conduction shell is provided with a liquid outlet connected with the other end of the heat dissipation liquid channel.
The utility model has the advantages that:
(1) the compact servo electro-hydraulic actuator does not need an additional pump station, has a small and compact structure, can realize a telescopic function to meet the use requirement, and is convenient and quick to install and maintain;
(2) the integrated valve group is connected with other components for control, so that the number of pipes exposed outside is reduced, and oil leakage points are not easy to generate.
Drawings
Fig. 1 is one of the schematic structural diagrams of the compact servo electro-hydraulic actuator of the present invention.
Fig. 2 is a second schematic structural diagram of the medium-compact servo electro-hydraulic actuator according to the present invention.
Fig. 3 is a schematic structural view of the integrated valve set of the present invention.
Fig. 4 is a schematic structural diagram of the middle heat dissipation module of the present invention.
Detailed Description
Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the invention, its application, or uses. The present invention may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not restrictive, unless specifically stated otherwise.
The use of "first," "second," and similar terms in the description herein do not denote any order, quantity, or importance, but rather the terms are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word comprises the element listed after the word, and does not exclude the possibility that other elements may also be included. "upper", "lower", "left", "right", and the like are used only to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
As shown in fig. 1 to 4, the compact servo electro-hydraulic actuator includes a hydraulic cylinder 23, an integrated valve group 26 is assembled on one side of the hydraulic cylinder 23, a bidirectional hydraulic pump 1 is assembled on the other side of the hydraulic cylinder 23, the bidirectional hydraulic pump 1 is in transmission connection with a servo motor 22, the operation of the bidirectional hydraulic pump 1 is precisely controlled by the servo motor 22, the bidirectional hydraulic pump 1 is connected with the integrated valve group 26 through a pump connection pipe 28, and the hydraulic cylinder 23 is connected with the integrated valve group 26; the compact servo electro-hydraulic actuator in the embodiment does not need an additional pump station, is small and compact in structure, and can realize a telescopic function to meet use requirements; the number of pipes exposed outside is reduced by connecting and controlling the integrated valve group 26 with other components, and oil leakage points are not easy to generate.
As shown in fig. 3, the hydraulic cylinder 23 has a front cylinder 2301 and a rear cylinder 2302, the front cylinder 2301 and the rear cylinder 2301 are coaxially connected, and a front piston 2305 is assembled in the front cylinder 2301; one side of the front piston 2305 close to the rear cylinder body 2302 is connected with a rear rod 2304, the rear rod is provided with a rear piston 2306, and the other side of the front piston 2305 is connected with a front rod 2303; the cavity in the rear cylinder 2302, which is close to the front cylinder 2301 and is partitioned by the rear piston 2306, is an A1 cavity 2307, the cavity in the front cylinder 2301, which is close to the rear cylinder 2302 and is partitioned by the front piston 2305, is an A2 cavity 2308, and the cavity in the front cylinder 2301, which is away from the rear cylinder 2302 and is partitioned by the front piston 2305, is an A3 cavity 2308; oil is fed into the cavity A2 2308, oil is discharged from the cavity A1 2307 and the cavity A3 2309, and the front cylinder body 2303 extends outwards to drive an external mechanism to act; conversely, the inside of the cavity A2 2308 is out, the cavity A1 2307 and the cavity A3 2309 are in, and the front cylinder 2303 is retracted inwards.
As a specific implementation manner of the integrated valve assembly in the above embodiment, as shown in fig. 2, the integrated valve assembly includes: the valve group body is provided with an A port, a B port, an A1 port, an A2 port and an A3 port, the A port and the B port are connected with the bidirectional hydraulic pump 1 through a pump connecting pipe 28, the A1 port is connected with the A1 cavity 2307, the A2 port is connected with the A2 cavity 2308, and the A3 port is connected with the A3 cavity 2309; an oil outlet of the first check valve is connected with the port A, and an oil inlet of the first check valve is connected with the port A3 through a fifth overflow valve; an oil outlet of the second one-way valve is connected with the port B, and an oil inlet of the second one-way valve is connected with an oil inlet of the first one-way valve; an oil inlet of the third one-way valve is connected with the port A2, an oil outlet of the third one-way valve is respectively connected with the port A, the port A2 and the port A3, and a sixth reversing valve is connected between the oil outlet of the third one-way valve and the port A3; an oil outlet of the fourth one-way valve is connected with the port A3, and an oil inlet of the fourth one-way valve is connected with an oil inlet of the third one-way valve; an oil inlet of the first overflow valve is connected with the port A, and an oil outlet of the first overflow valve is connected with an oil outlet of the first check valve; an oil inlet of the second overflow valve is connected with the port B, and an oil outlet of the second overflow valve is connected with an oil outlet of the first overflow valve; an oil inlet of the third overflow valve is connected with the port A2, and an oil outlet of the third overflow valve is connected with an oil inlet of the third one-way valve; an oil outlet of the fourth overflow valve is connected with the port A3 through a fourth reversing valve, an oil inlet of the fourth overflow valve is connected with two branches, one branch is connected with the port A1 through a pressure compensation flow control valve, and the other branch is connected with the port B through a fifth reversing valve and a third reversing valve in sequence; an oil inlet of the first reversing valve is connected with the port A2, and an oil outlet of the first reversing valve is connected with the port A; and an oil inlet of the second reversing valve is connected with the port A3, and an oil inlet is connected with the buckle B.
When the hydraulic actuator is used, the port A1, the port A2 and the port A3 are respectively connected with the cavity A1 2307, the cavity A2 2308 and the cavity A3 2309 of the hydraulic cylinder 23, and hydraulic oil is pumped into the port A2 and/or pumped out of the port A3 and the port A1 to drive the actuator to extend; hydraulic oil is pumped into the A1 and A3 ports and/or is pumped out of the A2 port to drive the front rod body 2303 to retract; this integrated valves can control executor pneumatic cylinder and realize multiple mode of action: when the actuator rapidly extends, the fifth reversing valve 15, the third reversing valve 13, the first reversing valve 11 and the sixth reversing valve 16 are electrified, the bidirectional hydraulic pump 1 is started, hydraulic oil is pumped into the A2 cavity 2308 from the A2 port under the action of the bidirectional hydraulic pump 1, meanwhile, the A1 cavity 2307 flows back from the A1 port hydraulic oil, the pressure of the fifth overflow valve 10 is increased and exceeds the set value of the fifth overflow valve, so that the fifth overflow valve rapidly discharges the hydraulic oil in the connecting cavity of the hydraulic cylinder 23 and the A3 port at a high flow rate, and the actuator rapidly extends; when the actuator slowly extends, the fifth reversing valve 15, the third reversing valve 13, the first reversing valve 11 and the second reversing valve 16 are electrified, the bidirectional hydraulic pump 1 is started, hydraulic oil is pumped into the A2 cavity 2308 of the hydraulic cylinder 23 from the A2 port under the action of the bidirectional hydraulic pump 1, meanwhile, the hydraulic oil at the A1 port flows back, and the hydraulic oil at the A3 port flows back through the second reversing valve 12, so that the actuator slowly extends; the cavity of the hydraulic cylinder 23 connected with the port A2 is pressurized, at the moment, the first to sixth reversing valves are all de-energized, the bidirectional hydraulic pump 1 stops, and the hydraulic oil in the cavity A2 2308 of the hydraulic cylinder 23 cannot flow out through the port A2, so that the pressure maintaining function is realized; the cavity 2308 of the a2 cavity of the hydraulic cylinder 23 and the cavity connected with the port a2 are decompressed, the fourth reversing valve is powered on, the rest reversing valves are powered off, the bidirectional hydraulic pump 1 stops, hydraulic oil in the hydraulic cylinder 23 flows into the valve group from the port A3, then flows into the hydraulic cylinder 23 from the port a2, and redundant hydraulic oil flows into the energy accumulator for temporary storage; and (3) rapidly retracting, wherein the fifth reversing valve 15, the third reversing valve 13, the fourth reversing valve 14 and the sixth reversing valve 16 are electrified, the bidirectional hydraulic pump 1 is started, the bidirectional hydraulic pump 1 pumps hydraulic oil into the hydraulic cylinder 23 from an A1 port and an A3 port, the hydraulic cylinder 23 flows out from an A2 port, the pressure of the third overflow valve 8 is gradually increased, and when a set value is reached, the hydraulic oil in a cavity connecting the hydraulic cylinder 23 and the A2 port is rapidly discharged at a high flow rate, so that the rapid retracting action of the actuator is realized.
Furthermore, the valve group body is provided with a filter 17, an oil inlet of the filter 17 is connected with the bidirectional hydraulic pump 1, an oil outlet is connected with an oil inlet of the first one-way valve 2, hydraulic oil passing through the filter 17 can be filtered in the hydraulic oil backflow process through the filter 17, impurities such as metal chips generated in the actuator operation process are filtered, and the actuator is guaranteed to normally operate.
Further, the valve group body is provided with an energy accumulator 18 and an SP port connected with the energy accumulator 18, the SP port is connected with an oil inlet of the first one-way valve 2, the energy accumulator 18 plays a role in buffering the internal pressure of the module and temporarily stores hydraulic oil when the hydraulic cylinder 23 relieves the pressure; the accumulator 18 is pre-charged with air pressure to prevent backflow of hydraulic oil in an initial state.
Furthermore, the valve group body is provided with an SP3 port connected with the first pressure sensor 19, an SP3 port is connected with an oil inlet of the first one-way valve 2, the first pressure sensor 19 can be installed at the SP3 port when the valve group is used, and the pressure value of the energy accumulator 18 is detected through the first pressure sensor 19; the valve set body is provided with an SP2 port connected with the second pressure sensor 20, an SP2 port is connected with an A1 port, the second pressure sensor can be connected with an SP2 port when the valve set is used, and the internal pressure of a connecting cavity of the hydraulic cylinder 23 and the A1 port is detected through the second pressure sensor 20; the valve block body has an SP1 port connected to the third pressure sensor 21, an SP1 port connected to an a2 port, and the third pressure sensor is connected to the SP3 port in use, and the third pressure sensor 21 detects the internal pressure of a chamber connecting the hydraulic cylinder 23 and the a2 port.
Furthermore, the first reversing valve 11, the second reversing valve 12, the third reversing valve 13 and the fourth reversing valve 14 are two-position three-way electromagnetic reversing valves; the first change valve 11 is used for controlling the cut-off and the conduction of the port A2 to the direction of the port A; the second direction switching valve 12 is used for controlling the connection and disconnection of the port A3 to the port B; the third reversing valve 13 is used for controlling the cut-off and the conduction of the fifth reversing valve 15 to the port B; the fourth direction valve 14 is used for controlling the connection and disconnection of the port A3 to the port A2; the fifth reversing valve 15 is a two-position communication and cutoff type electromagnetic reversing valve, and the fifth reversing valve 15 is used for controlling the cutoff and the conduction between the port A1 and the port B; the sixth switching valve 16 is a two-position four-solenoid switching valve, and the sixth switching valve 16 is used for switching the port a2 to the port A3.
As shown in fig. 1, the outside of the integrated valve group 26 is equipped with a heat dissipation module 27; more specifically, as shown in fig. 4, the heat dissipation module 27 has a heat conduction housing 2701 in contact connection with the integrated valve set 26, a heat dissipation liquid channel 2704 is provided inside the heat conduction housing 2701 for increasing the contact area between the cooling liquid and the heat conduction housing 271, one side of the heat conduction housing 2701 is provided with a liquid inlet 2702 connected to one end of the heat dissipation liquid channel 2704, the other side of the heat conduction housing 2701 is provided with a liquid outlet 2703 connected to the other end of the heat dissipation liquid channel 2704, when in use, the heat dissipation module is connected to an external device to pump the cooling liquid from the liquid inlet 2702 into the heat dissipation liquid channel 2704, and after heat exchange is completed, the cooling liquid flows out from the liquid outlet 2703, thereby achieving a heat dissipation effect.
Thus far, various embodiments of the present invention have been described in detail. Some details which are well known in the art have not been described in order to avoid obscuring the concepts of the present invention. Those skilled in the art can now fully appreciate how to implement the teachings disclosed herein, in view of the foregoing description.
The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.
Claims (10)
1. The utility model provides a compact servo electro-hydraulic actuator, its characterized in that includes the pneumatic cylinder, one side of pneumatic cylinder is equipped with integrated valves, the opposite side of pneumatic cylinder is equipped with two-way hydraulic pump, two-way hydraulic pump transmission is connected with servo motor, two-way hydraulic pump pass through the pump connecting pipe with integrated valves is connected, the pneumatic cylinder with integrated valves is connected.
2. The compact servo electro-hydraulic actuator of claim 1, wherein: the hydraulic cylinder is provided with a front cylinder body and a rear cylinder body, the front cylinder body is coaxially connected with the rear cylinder body, and a front piston is assembled in the front cylinder body; one side of the front piston, which is close to the rear cylinder body, is connected with a rear rod body, a rear piston is assembled on the rear rod body, and the other side of the front piston is connected with a front rod body; the rear cylinder body is internally provided with a cavity A1 which is separated by a rear piston and is close to one side of the front cylinder body, the front cylinder body is internally provided with a cavity A2 which is separated by a front piston and is close to one side of the rear cylinder body, and the cavity A3 is arranged on the other side of the front cylinder body.
3. The compact servo electro-hydraulic actuator of claim 2, wherein the integrated valve block has:
the valve block body is provided with an A port, a B port, an A1 port, an A2 port and an A3 port, the A port and the B port are connected with the bidirectional hydraulic pump through pump connecting pipes, the A1 port is connected with the A1 cavity, the A2 port is connected with the A2 cavity, and the A3 port is connected with the A3 cavity;
an oil outlet of the first check valve is connected with the port A, and an oil inlet of the first check valve is connected with the port A3 through a fifth overflow valve;
an oil outlet of the second one-way valve is connected with the port B, and an oil inlet of the second one-way valve is connected with an oil inlet of the first one-way valve;
an oil inlet of the third one-way valve is connected with the port A2, an oil outlet of the third one-way valve is respectively connected with the port A, the port A2 and the port A3, and a sixth reversing valve is connected between the oil outlet of the third one-way valve and the port A3;
an oil outlet of the fourth one-way valve is connected with the port A3, and an oil inlet of the fourth one-way valve is connected with an oil inlet of the third one-way valve;
an oil inlet of the first overflow valve is connected with the port A, and an oil outlet of the first overflow valve is connected with an oil outlet of the first one-way valve;
an oil inlet of the second overflow valve is connected with the port B, and an oil outlet of the second overflow valve is connected with an oil outlet of the first overflow valve;
an oil inlet of the third overflow valve is connected with the port A2, and an oil outlet of the third overflow valve is connected with an oil inlet of the third one-way valve;
an oil outlet of the fourth overflow valve is connected with the port A3 through a fourth reversing valve, an oil inlet of the fourth overflow valve is connected with two branches, one branch is connected with the port A1 through a pressure compensation flow control valve, and the other branch is connected with the port B through a fifth reversing valve and a third reversing valve in sequence;
the oil inlet of the first reversing valve is connected with the port A2, and the oil outlet of the first reversing valve is connected with the port A;
and an oil inlet of the second reversing valve is connected with the port A3, and an oil inlet of the second reversing valve is connected with the button B.
4. The compact servo electro-hydraulic actuator of claim 3, wherein: the valve group body is further provided with a filter, an oil inlet of the filter is connected with the bidirectional hydraulic pump, and an oil outlet of the filter is connected with an oil inlet of the first one-way valve.
5. The compact servo electro-hydraulic actuator of claim 3, wherein: the valve group body is provided with an energy accumulator and an SP (service provider) port connected with the energy accumulator, and the SP port is connected with an oil inlet of the first one-way valve.
6. The compact servo electro-hydraulic actuator of claim 5, wherein: the accumulator is pre-charged with air pressure.
7. The compact servo electro-hydraulic actuator of claim 3, wherein: the valve group body is provided with a first pressure sensor and an SP3 port connected with the first pressure sensor, and the SP3 port is connected with an oil inlet of the first one-way valve; the valve group body is provided with a second pressure sensor and an SP2 port connected with the second pressure sensor, and the SP2 port is connected with the A1 port; the valve group body is provided with a third pressure sensor and an SP1 port connected with the third pressure sensor, and the SP1 port is connected with the A2 port.
8. The compact servo electro-hydraulic actuator of claim 3, wherein: the first reversing valve, the second reversing valve, the third reversing valve and the fourth reversing valve are two-position three-way electromagnetic reversing valves; the fifth reversing valve is a two-position communication cut-off type electromagnetic reversing valve; and the sixth reversing valve is a two-position four-electromagnetic reversing valve.
9. The compact servo electro-hydraulic actuator of claim 1, wherein: and a heat dissipation module is assembled on the outer side of the integrated valve group.
10. The compact servo electro-hydraulic actuator of claim 9, wherein: the heat dissipation module is provided with a heat conduction shell connected with the integrated valve group in a contact manner, a heat dissipation liquid channel is formed in the heat conduction shell, one side of the heat conduction shell is provided with a liquid inlet connected with one end of the heat dissipation liquid channel, and the other side of the heat conduction shell is provided with a liquid outlet connected with the other end of the heat dissipation liquid channel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122562601.XU CN217056541U (en) | 2021-10-25 | 2021-10-25 | Compact servo electro-hydraulic actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122562601.XU CN217056541U (en) | 2021-10-25 | 2021-10-25 | Compact servo electro-hydraulic actuator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN217056541U true CN217056541U (en) | 2022-07-26 |
Family
ID=82475730
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122562601.XU Active CN217056541U (en) | 2021-10-25 | 2021-10-25 | Compact servo electro-hydraulic actuator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN217056541U (en) |
-
2021
- 2021-10-25 CN CN202122562601.XU patent/CN217056541U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100549431C (en) | Fluid pressure valve device | |
| JP2010048332A (en) | Hydraulic pressure circuit | |
| CN217056541U (en) | Compact servo electro-hydraulic actuator | |
| CN213682287U (en) | Steering hydraulic system and loader | |
| CN112983909B (en) | Movable arm hydraulic system | |
| CN110332172B (en) | Hydraulic actuator with power unit internally arranged in hydraulic rod | |
| CN113932058A (en) | Compact servo electro-hydraulic actuator | |
| CN109306976B (en) | Load sensitive control system | |
| CN107524641B (en) | Independent integrated hydraulic linear driving system | |
| CN106812752B (en) | Multiple directional control valve | |
| CN211550114U (en) | Pressurizing hydraulic system | |
| WO2021114668A1 (en) | Open hydraulic pump and open hydraulic system | |
| CN216407328U (en) | Integrated valve group of actuator | |
| CN108266413B (en) | Asymmetric electro-hydrostatic actuator based on pressure selection valve | |
| CN209925316U (en) | Automatic continuous single-action supercharging device | |
| CN218236329U (en) | Valve electrohydraulic driving device | |
| CN210371407U (en) | Quantitative compound control hydraulic system and engineering machinery | |
| CN101624977B (en) | Pneumatic oil pump | |
| CN216447206U (en) | Hydraulic control system of metal chip forming machine | |
| CN110630582A (en) | Cylinder energy storage type hydraulic cylinder | |
| CN214196806U (en) | Hydraulic system of concrete pump | |
| CN216842426U (en) | Hydraulic control reversing valve with pilot oil way | |
| CN212643238U (en) | Tunnel vehicle oil circuit system with heat dissipation device | |
| CN213109295U (en) | Hydraulic brake system | |
| CN213744206U (en) | Device for improving stability and efficiency of engineering machinery load sensitive hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |