CN201650928U - Hydraulic system - Google Patents
Hydraulic system Download PDFInfo
- Publication number
- CN201650928U CN201650928U CN2010201345016U CN201020134501U CN201650928U CN 201650928 U CN201650928 U CN 201650928U CN 2010201345016 U CN2010201345016 U CN 2010201345016U CN 201020134501 U CN201020134501 U CN 201020134501U CN 201650928 U CN201650928 U CN 201650928U
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- Prior art keywords
- oil
- back cavity
- hydraulic system
- ante
- chamber
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- 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.)
- Expired - Lifetime
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- 239000002828 fuel tank Substances 0.000 claims description 15
- 238000000034 method Methods 0.000 abstract description 12
- 239000003921 oil Substances 0.000 description 70
- 239000010720 hydraulic oil Substances 0.000 description 8
- 238000000605 extraction Methods 0.000 description 6
- 230000002950 deficient Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
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- Fluid-Pressure Circuits (AREA)
Abstract
The utility model provides a hydraulic system, which comprises an oil tank, an oil pump, a pressure boosting tank, a front cavity oil inlet passage, a front cavity oil return passage, a back cavity oil inlet passage, a first back cavity oil return passage and a second back cavity oil return passage, wherein the oil pump is communicated with the oil tank, the pressure boosting cylinder is provided with a front cavity and a back cavity which are separated by a piston, the front cavity oil inlet passage and the front cavity oil return passage are connected between the oil pump and the front cavity of the pressure boosting cylinder, the back cavity oil inlet passage and the first back cavity oil return passage are connected between the oil pump and the back cavity of the pressure boosting cylinder, and the second back cavity oil return passage is connected between the back cavity of the pressure boosting cylinder and the oil tank. Through the provided hydraulic system, the oil path in the oil discharge and pressure relief process is effectively separated from the main oil paths of equipment, the oil discharge and pressure relief process is accelerated, the time for bearing high pressure by the system is greatly shortened, so the hydraulic system is effectively prevented from being damaged because the hydraulic system is in the high-pressure state for a long time.
Description
Technical field
The utility model relates to hydraulic system, relates in particular to the hydraulic system that is used for hydraulic riveter.
Background technique
In the process of automobile making, need use riveting technology (such as automobile frame is carried out rivet) through regular meeting, wherein the most frequently used is hydraulic efficiency riveting.When a bogie frame is riveted; usually need riveting equipment to be in and do not shut down operating condition; thereby the high-voltage oil cylinder in the hydraulic system of using in the hydraulic efficiency riveting process need be in high pressure conditions for a long time, bears high pressure, and this makes that each parts of hydraulic system all are more prone to damage.And for employed hydraulic system, no matter reprocess or change, cost is all than higher, and frequent damage and maintenance also can bring very big inconvenience to production process.
In the existing hydraulic efficiency riveting system, be in high pressure conditions for a long time for fear of system, after finishing once riveted joint task, the oil in the oil cylinder can be flow back in the oil pump through oil pipe, thereby the pressure in the mitigation system, but the oil extraction pressure leak process in the existing system adopts the oil-feed oil circuit to come oil return (coming the control oil channel direction with solenoid directional control valve), do the speed that can influence the oil extraction pressure release like this, thereby the time of high pressure is born by the increase system.
The model utility content
For solve the oil extraction speed that exists in the existing hydraulic system break down slowly and easily and cause can't oil extraction defective, the utility model proposes a kind of improved hydraulic system.
The utility model provides a kind of hydraulic system, and this hydraulic system comprises: fuel tank; Oil pump, described oil pump is connected with described fuel tank; Pressurized cylinder, this pressurized cylinder have the ante-chamber and the back cavity of being separated by by piston; Ante-chamber oil-feed path is connected between the ante-chamber of described oil pump and described pressurized cylinder; The ante-chamber way to cycle oil is connected between the ante-chamber of described oil pump and described pressurized cylinder; Back cavity oil-feed path is connected between the back cavity of described oil pump and described pressurized cylinder; The first back cavity way to cycle oil is connected between the back cavity of described oil pump and described pressurized cylinder; This hydraulic system also comprises the second back cavity way to cycle oil, and this second back cavity way to cycle oil directly is connected between the back cavity and described fuel tank of described pressurized cylinder.
By the hydraulic system that the utility model proposes, on the basis of existing oil circuit, increased by the second back cavity way to cycle oil that directly is connected between pressurized cylinder and the fuel tank in addition, thereby carried out separating effectively between the main oil circuit of the oil circuit that makes the oil extraction pressure leak process and equipment, accelerated the oil extraction pressure leak process, the time that makes system bear high pressure reduces greatly, thereby has avoided hydraulic system to be in high pressure conditions for a long time and to cause damage easily effectively.
Description of drawings
Fig. 1 shows the structural drawing according to a kind of hydraulic system of mode of execution.
Embodiment
Fig. 1 shows the hydraulic system according to a kind of mode of execution of the present utility model.
As shown in Figure 1, this hydraulic system comprises: fuel tank 2; Oil pump 3; Pressurized cylinder 1, this pressurized cylinder 1 have the ante-chamber 5 and the back cavity 4 of being separated by by piston; There are ante-chamber oil-feed path (D-V2-V3-C) and ante-chamber way to cycle oil (A-V1-E) between the ante-chamber 5 of wherein said oil pump 3 and described pressurized cylinder 1, there are the back cavity oil-feed path (D-V2-B) and the first back cavity way to cycle oil (B-V2-E) between the back cavity 4 of described oil pump 3 and described pressurized cylinder 1, can be connected by oil circuit between wherein said oil pump 3 and the described fuel tank 2, this hydraulic system also comprises the back cavity 4 that directly is connected described pressurized cylinder 1 and the second back cavity way to cycle oil (B-V4-F) between the described fuel tank 2.
In Fig. 1, A-F represents hydraulic fluid port respectively, and wherein A and C are positioned at the ante-chamber 5 of pressurized cylinder, and B is positioned at the back cavity 4 of pressurized cylinder, and D and E are positioned on the oil pump 3, and F is positioned on the fuel tank 2, and V1, V2 and V3 are the identification point on the oil circuit, is used for assisting oil circuit is indicated.
Described hydraulic system also comprises a plurality of solenoid valves, and each solenoid valve in wherein said a plurality of solenoid valves is connected on one in described ante-chamber oil-feed path, described ante-chamber way to cycle oil, described back cavity oil-feed path, the described first back cavity way to cycle oil and the described second back cavity way to cycle oil.Described solenoid valve is preferably solenoid directional control valve.
For example, in hydraulic system shown in Figure 1, comprise a 3-position 4-way solenoid directional control valve 9 and two one two energising magnetic selector valve 10, they are respectively applied for controls each oil-feed path and way to cycle oil, particularly, 3-position 4-way solenoid directional control valve 9 is used to control ante-chamber oil-feed path (D-V2-V3-C), ante-chamber way to cycle oil (A-V1-E), the unlatching and the closure of the back cavity oil-feed path (D-V2-B) and the first back cavity way to cycle oil (B-V2-E), in a unlatching and the closure that is used to control back cavity oil-feed path (D-V2-B) and the first back cavity way to cycle oil (B-V2-E) in described two one two energising magnetic selector valve 10, described two one two magnetic selector valve 10 of switching on another is used to control the unlatching and the closure of the second back cavity way to cycle oil (B-V4-F).
Described hydraulic system can also comprise one-way valve 7, and this one-way valve 7 is connected in ante-chamber oil-feed path (D-V2-V3-C), is used to control the oil-feed to ante-chamber.
Described hydraulic system also comprises the hydraulic pressure output unit, and this hydraulic pressure output unit is connected to the ante-chamber of described pressurized cylinder by oil circuit.
Described hydraulic system also comprises at least one pressure relay, and described at least one pressure relay is connected on the oil circuit between described pressurized cylinder and the described hydraulic pressure output unit.Described at least one pressure relay is used for control pressurized cylinder is pressurizeed and/or pressure release, and the unlatching of control electromagnetic valve and/or close.Wherein can adopt different pressure relayes to control respectively, can also carry out the control of the overall situation with a pressure relay to the pressurization of pressurized cylinder and the switching of solenoid valve.
In mode of execution shown in Figure 1, described hydraulic system comprises first pressure relay 6 and second pressure relay 6 ', described first pressure relay 6 is connected on the oil circuit between described pressurized cylinder 1 and the described hydraulic pressure output unit 8, by the pressure in the oil circuit between described pressurized cylinder 1 and the described hydraulic pressure output unit 8 is detected, the back cavity 4 of controlling two one two energising magnetic selector valve 10 pairs of described pressurized cylinders 1 pressurizes/or pressure release.
Described second pressure relay 6 ' is connected on the oil circuit between described pressurized cylinder 1 and the described hydraulic pressure output unit 8, by the pressure in the oil circuit between described pressurized cylinder 1 and the described hydraulic pressure output unit 8 is detected, control the closure or openness of described solenoid directional control valve 9.
Though it is pointed out that the back cavity oil-feed path (D-V2-B) and the first back cavity way to cycle oil (B-V2-E) in the present embodiment are same oil circuits, in other mode of execution, can select to use two oil circuits or an oil circuit as the case may be.
Below in conjunction with Fig. 1 the operating process of hydraulic system is described.
When operation, at first, oil pump 3 is started working, hydraulic oil is entered solenoid directional control valve N1 from fuel tank 2 sucking-offs, ante-chamber hydraulic oil process ante-chamber oil-feed path (D-V2-V3-C) enters the ante-chamber 5 and the clutch release slave cylinder back cavity of pressurized cylinder 1, and pressurized cylinder back cavity hydraulic oil enters the back cavity 4 (this moment, N3 closed towards the oil outlet of fuel tank 2) of pressurized cylinder 1 by back cavity oil-feed path (D-V2-B).
Subsequently, under the control of first pressure relay 6,, promote piston motion to back cavity 4 superchargings of pressurized cylinder 1.Thereby ante-chamber hydraulic oil is ejected (this moment, the oil return port of N1 was closed), ante-chamber hydraulic oil enters hydraulic pressure output unit 8 inside by pipeline, thereby promote piston rivet is implemented riveted joint.
After rivet is finished, 9 commutations of second pressure relay, 6 ' control 3-position 4-way solenoid directional control valve, cylinder 8 ante-chambers that push the work forward return, make chamber, pressurized cylinder front and back hydraulic oil return oil pump 3 (pressing oil pump 3 reasonable storages sets) through the first back cavity way to cycle oil (B-V2-E) respectively, and directly return fuel tank 2 through the second back cavity way to cycle oil (B-V4-F), and owing to the back cavity pressure reduces, piston between ante-chamber and the back cavity descends, thereby make the piston in the hydraulic pressure output unit 8 return, hydraulic oil returns pressurized cylinder 1 (this moment, one-way valve 7 was closed) from oil transport pipeline, and part ante-chamber hydraulic oil returns oil pump 3 by ante-chamber way to cycle oil (A-V1-E), like this, system has just finished once-through operation.
By hydraulic system pressure relief device and the corresponding hydraulic system that the utility model proposes, proposed directly to be connected the way to cycle oil between pressurized cylinder and the fuel tank, thereby carried out separating effectively between the main oil circuit of the oil circuit that makes pressure leak process and equipment, accelerated pressure leak process, the time that makes system bear high pressure reduces greatly, thereby has avoided hydraulic system to be in high pressure conditions for a long time and to cause damage easily effectively.
Claims (7)
1. hydraulic system, this hydraulic system comprises:
Fuel tank;
Oil pump, described oil pump is connected with described fuel tank;
Pressurized cylinder, this pressurized cylinder have the ante-chamber and the back cavity of being separated by by piston;
Ante-chamber oil-feed path is connected between the ante-chamber of described oil pump and described pressurized cylinder;
The ante-chamber way to cycle oil is connected between the ante-chamber of described oil pump and described pressurized cylinder;
Back cavity oil-feed path is connected between the back cavity of described oil pump and described pressurized cylinder;
The first back cavity way to cycle oil is connected between the back cavity of described oil pump and described pressurized cylinder;
It is characterized in that this hydraulic system also comprises the second back cavity way to cycle oil, this second back cavity way to cycle oil is connected between the back cavity and described fuel tank of described pressurized cylinder.
2. hydraulic system according to claim 1 is characterized in that, described back cavity oil-feed path and the described first back cavity way to cycle oil are same oil circuits.
3. hydraulic system according to claim 1 and 2, it is characterized in that, described hydraulic system also comprises a plurality of solenoid valves, all is connected with one or more in described a plurality of solenoid valve on every path in wherein said ante-chamber oil-feed path, described ante-chamber way to cycle oil, described back cavity oil-feed path, the described first back cavity way to cycle oil and the described second back cavity way to cycle oil.
4. hydraulic system according to claim 3 is characterized in that described solenoid valve is a solenoid directional control valve.
5. hydraulic system according to claim 1 and 2 is characterized in that described hydraulic system also comprises one-way valve, and this one-way valve is positioned on the described ante-chamber oil-feed path.
6. hydraulic system according to claim 1 and 2 is characterized in that described hydraulic system also comprises the hydraulic pressure output unit, and this hydraulic pressure output unit is connected to the ante-chamber of described pressurized cylinder by oil circuit.
7. hydraulic system according to claim 6 is characterized in that described hydraulic system also comprises at least one pressure relay, and described at least one pressure relay is connected on the oil circuit between described pressurized cylinder and the described hydraulic pressure output unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201345016U CN201650928U (en) | 2010-03-15 | 2010-03-15 | Hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201345016U CN201650928U (en) | 2010-03-15 | 2010-03-15 | Hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201650928U true CN201650928U (en) | 2010-11-24 |
Family
ID=43116163
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010201345016U Expired - Lifetime CN201650928U (en) | 2010-03-15 | 2010-03-15 | Hydraulic system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201650928U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734267A (en) * | 2011-04-14 | 2012-10-17 | 伯尔霍夫连接技术有限公司 | Hydraulically operated setting device with a hydraulic aggregate and a joining method for connecting at least two components |
| CN104214146A (en) * | 2013-05-30 | 2014-12-17 | 广东科达洁能股份有限公司 | Novel pressurized hydraulic device |
| CN104776002A (en) * | 2015-04-22 | 2015-07-15 | 宁波市鄞州中天液压有限公司 | Integrated type ultrahigh-pressure booster pump |
| CN116104741A (en) * | 2022-12-14 | 2023-05-12 | 三一氢能有限公司 | Hydraulic drive piston compressor system and shutdown method and device thereof, and hydrogenation station |
-
2010
- 2010-03-15 CN CN2010201345016U patent/CN201650928U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734267A (en) * | 2011-04-14 | 2012-10-17 | 伯尔霍夫连接技术有限公司 | Hydraulically operated setting device with a hydraulic aggregate and a joining method for connecting at least two components |
| US9149862B2 (en) | 2011-04-14 | 2015-10-06 | Bollhoff Verbindungstechnik Gmbh | Hydraulically operated setting device with a hydraulic aggregate and a joining method for connecting at least two components |
| CN102734267B (en) * | 2011-04-14 | 2016-12-14 | 伯尔霍夫连接技术有限公司 | Hydraulic operation assembling device with hydraulic package and the method for attachment of connection at least two element |
| CN104214146A (en) * | 2013-05-30 | 2014-12-17 | 广东科达洁能股份有限公司 | Novel pressurized hydraulic device |
| CN104214146B (en) * | 2013-05-30 | 2017-08-04 | 广东科达洁能股份有限公司 | Pressurization hydraulic device |
| CN104776002A (en) * | 2015-04-22 | 2015-07-15 | 宁波市鄞州中天液压有限公司 | Integrated type ultrahigh-pressure booster pump |
| CN116104741A (en) * | 2022-12-14 | 2023-05-12 | 三一氢能有限公司 | Hydraulic drive piston compressor system and shutdown method and device thereof, and hydrogenation station |
| CN116104741B (en) * | 2022-12-14 | 2023-09-15 | 三一氢能有限公司 | Hydraulic drive piston compressor system and shutdown method and device thereof, and hydrogenation station |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20101124 |