CN204226324U - A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration - Google Patents
A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration Download PDFInfo
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- CN204226324U CN204226324U CN201420710223.2U CN201420710223U CN204226324U CN 204226324 U CN204226324 U CN 204226324U CN 201420710223 U CN201420710223 U CN 201420710223U CN 204226324 U CN204226324 U CN 204226324U
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Abstract
The utility model relates to a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration, comprises the combined type reversal valve group be located between oiling valve and scavenger valve; Each valve body is provided with attachment hole, double threaded screw through attachment hole and nut screw connection fastening; Being interconnected by being located at the parallel port of side, middle bit port and low-pressure channel between each valve body, forming complete hydraulic control oil circuit; The linear compensation sealing configuration that the hydraulic fluid port of each passage all adopts seal groove and Sealing to form, seal groove is circular deep gouge, and its central authorities communicate with hydraulic fluid port, and the bottom land of seal groove be skewed, the seal groove degree of depth by center to close groove side wall dimension linear increase; Sealing is circular ring-type Sealing, and the sidewall of its excircle and described seal groove is close to.Canned linear compensation rate of the present utility model can meet the resiliently deformable rate of double threaded screw under impacting with high pressure operating mode, and can eliminate the hidden danger that Sealing is inhaled into oil duct, realizes the high reliability of sealing.
Description
Technical field
The utility model relates to hydraulic circuit control unit, is specifically related to a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration.It is the Combined hydraulic valve that application hydraulic control technology can regulate the conversion of fluid moving direction, system pressure, is widely used in all kinds of small engineering machinery, railway machinery, highway machinery, building machinery, mining machinery, boring mechanic, environmental sanitation machinery, farm machinery etc.
Background technique
Small-sized hydraulic combination brake switch and proporting has the advantages that structure is simple, volume compact, pressure and range of flow are moderate, applied widely, easy for installation, is widely used in small-sized walking class hydraulic machinery as hydraulic control component.
Conventional ZS-L10, ZFS-L10, SC3A-F12 combination brake switch and proporting and the installation of small-sized integral type multi-way valve at present uses, disclosed in CN 201763716 U " a kind of economical and efficient type multi-way valve ", comprise the combined type reversal valve group be located between oiling valve and scavenger valve, each guiding valve of combined type reversal valve group is respectively equipped with the one-way valve preventing fluid from flowing backwards; Each guiding valve of described oiling valve, combined type reversal valve group and the valve body of scavenger valve are provided with four corresponding attachment holes, four double threaded screws are each passed through attachment hole corresponding on each valve body, fastening with nut screw connection, each guiding valve of oiling valve, combined type reversal valve group and scavenger valve are connected as one; Being interconnected by being located at the parallel port of side, middle bit port and low-pressure channel between each guiding valve of described oiling valve, combined type reversal valve group and scavenger valve, forming complete hydraulic control oil circuit.This multi-way valve compact structure, good manufacturability, pressure are high, flow is large, have the function switching liquid flow path direction, adjustable control system pressure and prevent fluid from flowing backwards, applied widely, economical and efficient, it is convenient to safeguard, can meet and have a large capacity and a wide range, without in Special controlling demand, the controlling functions requirement of high-pressure hydraulic machines, but remain in following defect: the right angle deep gouge structural type that the seal with O ring groove structural type due to passage place each between its valve pack all adopts Sealing NBS to recommend and size, its bottom surface is plane structure, the precompressed amount of Sealing is made to be a steady state value, its sealability decays with the increase of compensation rate, under conventional operating mode, there is reliability, but high pressure combination brake switch and proporting is under load behavior, impact by hydraulic shock variable is very large, its resiliently deformable rate connecting the double threaded screw of combination brake switch and proporting group may exceed the effective compensation ability of sealing, now leak generation seal failure fluid accident.In addition, in order to reduce lifting surface area between valve body sheet, the rectangular seal groove that seal groove often adopts inner edge to communicate with each passage hydraulic fluid port designs, and because of the effect by oil duct adsorption force, Sealing has the hidden danger being inhaled into oil duct, and happens occasionally.
For these reasons, need for the reliable minitype high-performance combination brake switch and proporting of numerous small-sized hydraulic machinery a kind of sealability of development.
Summary of the invention
The purpose of this utility model is to provide a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration, its canned linear compensation rate can meet the resiliently deformable rate of double threaded screw under impacting with high pressure operating mode, and the hidden danger that Sealing is inhaled into oil duct can be eliminated, realize the high reliability of sealing.
A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration described in the utility model, comprise the combined type reversal valve group be located between oiling valve and scavenger valve, each guiding valve of combined type reversal valve group is respectively equipped with the one-way valve preventing fluid from flowing backwards; Each guiding valve of described oiling valve, combined type reversal valve group and the valve body of scavenger valve are provided with four corresponding attachment holes, four double threaded screws are each passed through attachment hole corresponding on each valve body, fastening with nut screw connection, each guiding valve of oiling valve, combined type reversal valve group and scavenger valve are connected as one; Being interconnected by being located at the parallel port of side, middle bit port and low-pressure channel between each guiding valve of described oiling valve, combined type reversal valve group and scavenger valve, forming complete hydraulic control oil circuit; It is characterized in that: the linear compensation sealing configuration that the hydraulic fluid port of the parallel port of each valve body side, middle bit port and low-pressure channel all adopts seal groove and Sealing to form, described seal groove is circular deep gouge, its central authorities communicate with hydraulic fluid port, the bottom land of seal groove is skewed, and the seal groove degree of depth is increased near groove side wall dimension linear by center; Described Sealing is circular ring-type Sealing, and the sidewall of its excircle and described seal groove is close to.
Further, the angle α between the bottom land of described seal groove and horizontal plane is 6 ° ~ 8 °.
Further, described combined type reversal valve group is made up of 1 ~ 10 guiding valve; Described guiding valve is O type function reversing valve, y-function selector valve, Type B function reversing valve or N-type function reversing valve.
Further, the overflow overload valve of regulable control pressure is provided with in described oiling valve.
The utility model tool has the following advantages: by improving seal groove structure, by the floor design of seal groove be tilt, the seal groove degree of depth by center near groove side wall dimension linear increase, the precompressed amount of the Sealing in seal groove is also linearly increased to excircle gradually by inner circumference, namely Sealing precompression increases gradually, make the canned linear compensation rate of the Sealing of combination brake switch and proporting can meet the resiliently deformable rate of double threaded screw under impacting with high pressure operating mode, when the distortion of double threaded screw increases, can suitably be discharged to compensate its amount of deformation by the Sealing compressed.Because the precompressed amount of the Sealing in seal groove linearly increases to excircle gradually by by inner circumference, when Sealing excircle namely near the precompressed quantity not sufficient at groove side wall position to compensate the amount of deformation of double threaded screw time, namely Sealing inner circumference still can compensate its amount of deformation away from the precompressed amount at groove side wall position, still ensure that the sealing effect of Sealing.In addition, the linear tilt structure of this Sealing bottom surface, achieves the effect be firmly limited in by Sealing in seal groove, avoids the hidden danger that Sealing is inhaled into oil duct, ensure that the high reliability sealed between valve body sheet.
Accompanying drawing explanation
Fig. 1 is shape assumption diagram of the present utility model.
Fig. 2 is the K direction view of Fig. 1.
Fig. 3 is the D-D sectional drawing of Fig. 1.
Fig. 4 is the valve group junction surface hydraulic fluid port sealing distribution map of Fig. 1.
Fig. 5 is the E-E sectional view of Fig. 4.
Fig. 6 is hydraulic schematic diagram of the present utility model.
In figure: 1-oiling valve, 2-O type function reversing valve, 3-Y type function reversing valve, 4-B type function reversing valve, 5-N type function reversing valve, 6-scavenger valve, 7-double threaded screw, 8-nut, 9-parallel port, bit port in 10-, 11-low-pressure channel, 12-overload valve, 13-one-way valve, 14-pressure oil duct, 15-works oil duct, 16-valve internal channel, 17-Sealing, 18-seal groove.
Embodiment
Below in conjunction with accompanying drawing, the utility model is further described.
embodiment one
As shown in Fig. 1 ~ Fig. 6, a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration, comprise the combined type reversal valve group be located between oiling valve 1 and scavenger valve 6, described combined type reversal valve group is made up of four guiding valves that (number of guiding valve is at 1 ~ 10, determine according to specific product type), described guiding valve is O type function reversing valve 2, y-function selector valve 3, Type B function reversing valve 4 or N-type function reversing valve 5.Each guiding valve of combined type reversal valve group is respectively equipped with the one-way valve 13 preventing fluid from flowing backwards.
The valve body of described oiling valve 1, each guiding valve of combined type reversal valve group and scavenger valve 6 is provided with four corresponding attachment holes, four double threaded screws 7 are each passed through attachment hole corresponding on each valve body, coordinate fastening with nut 8, each guiding valve of oiling valve 1, combined type reversal valve group and scavenger valve 6 are connected as one; Described oiling valve 1, to be interconnected by being located at the parallel port 9 of side, meta path 10 and low-pressure channel 11 between each guiding valve of combined type reversal valve group and scavenger valve 6, to form complete hydraulic control oil circuit; The linear compensation sealing configuration that the hydraulic fluid port of the parallel port of each valve body side, middle bit port and low-pressure channel all adopts seal groove and Sealing to form, described seal groove 18 is circular deep gouge, its central authorities communicate with hydraulic fluid port, the bottom land of seal groove is skewed, angle α between the bottom land of seal groove and horizontal plane is 7 °, and the seal groove degree of depth is increased near groove side wall dimension linear by center; Described Sealing 17 is circular ring-type Sealing, and the sidewall of its excircle and described seal groove is close to.
The overflow overload valve 12 of regulable control pressure is provided with in described oiling valve 1.
Hydraulic principle of the present utility model: Fig. 1 and Fig. 3 is the utility model when being in neutral position, and the meta path 10 that pressure oil is communicated with each other through combined type reversal valve group after the pressure oil port P of oiling valve 1 enters returns fuel tank through scavenger valve 6 from hydraulic fluid port T.Thread type overflow overload valve 12 is equipped with in one end of oiling valve 1, for the regulation and control to system oil hydraulic coupling, and owing to having the function of Fill valve, can when system produces vacuum by drainback passage to the repairing of pressure oil duct, anti-locking system produces vibration and executive component and produces and vibrate creeping phenomenon.
See Fig. 4, combined type reversal valve group working principle:
(1) when O type function reversing valve 2 commutates left, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P oil inlet passage in valve is opened one-way valve and flowed into work oil duct 15 from pressure oil duct 14, enters executive component one end active chamber through hydraulic fluid port A1.The oil return of the executive component the other end active chamber simultaneously returned from hydraulic fluid port B1 enters scavenger valve 6 through valve internal channel 16 from low-pressure channel 11 and returns fuel tank through hydraulic fluid port T.
When O type function reversing valve 2 commutates to the right, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P oil inlet passage in valve is opened one-way valve and entered valve internal channel 16 from pressure oil duct 14, enters executive component the other end active chamber through hydraulic fluid port B1.Entering scavenger valve 6 from the work oil duct 15 of oil return in valve of executive component one end active chamber that hydraulic fluid port A1 returns from low-pressure channel 11 returns fuel tank through hydraulic fluid port T simultaneously.
When O type function reversing valve 2 is in Fig. 3 neutral position, the oil circuit of neutral path 10 is in unloading condition, oil inlet passage in valve, drainback passage, passage between actuator port A1, B1 are all closed, and the two ends active chamber of executive component is closed, and executive component is remained static.
(2) when y-function selector valve 3 commutates left, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component one end active chamber through valve internal channel from hydraulic fluid port A2.The oil return of the executive component the other end active chamber simultaneously returned from hydraulic fluid port B2 enters scavenger valve 6 through valve internal channel from low-pressure channel 11 and returns fuel tank through hydraulic fluid port T.
When y-function selector valve 3 commutates to the right, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component the other end active chamber through valve internal channel from hydraulic fluid port B2.Entering scavenger valve 6 through valve internal channel from low-pressure channel 11 from the oil return of executive component one end active chamber that hydraulic fluid port A2 returns returns fuel tank through hydraulic fluid port T simultaneously.
When y-function selector valve 3 is in Fig. 4 neutral position, the oil circuit of neutral path 10 is in unloading condition, oil inlet passage in valve is closed, drainback passage and the passage between actuator port A2, B2 are interconnected, the two ends active chamber of executive component and drainback passage are linked up, and make executive component be in quick condition.
(3) when Type B function reversing valve 4 commutates left, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component one end active chamber through valve internal channel from hydraulic fluid port A3.The oil return of the executive component the other end active chamber simultaneously returned from hydraulic fluid port B3 enters scavenger valve 6 through valve internal channel from low-pressure channel 11 and returns fuel tank through hydraulic fluid port T.
When Type B function reversing valve 4 commutates to the right, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component the other end active chamber through valve internal channel from hydraulic fluid port B3.Entering scavenger valve 6 through valve internal channel from low-pressure channel 11 from the oil return of executive component one end active chamber that hydraulic fluid port A3 returns returns fuel tank through hydraulic fluid port T simultaneously.
When Type B function reversing valve 4 is in Fig. 4 neutral position, the oil circuit of neutral path 10 is in unloading condition, oil inlet passage in valve and actuator port A3 are closed, passage between drainback passage and actuator port B3 is connected, and one end active chamber of executive component and drainback passage are linked up and be in unloading condition.
(4) when N-type function reversing valve 5 commutates left, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component one end active chamber through valve internal channel from hydraulic fluid port A4.The oil return of the executive component the other end active chamber simultaneously returned from hydraulic fluid port B4 enters scavenger valve 6 through valve internal channel from low-pressure channel 11 and returns fuel tank through hydraulic fluid port T.
When N-type function reversing valve 5 commutates to the right, the off-load oil circuit of neutral path 10 is cut off, and pressure oil P enters executive component the other end active chamber through valve internal channel from hydraulic fluid port B4.Entering scavenger valve 6 through valve internal channel from low-pressure channel 11 from the oil return of executive component one end active chamber that hydraulic fluid port A4 returns returns fuel tank through hydraulic fluid port T simultaneously.
When N-type function reversing valve 5 is in Fig. 4 neutral position, the oil circuit of neutral path 10 is in unloading condition, oil inlet passage in valve and actuator port B4 are closed, passage between drainback passage and actuator port A4 is connected, and one end active chamber of executive component and drainback passage are linked up and be in unloading condition.
Above-mentioned (1) to (4) group parallel connection type oil circuit selector valve group all can handle use individually or simultaneously, and when all not working, pressure oil P directly returns fuel tank off-load from scavenger valve 6 through hydraulic fluid port T through the neutral path 10 of each selector valve group.
embodiment two
Angle α between the bottom land of described seal groove and horizontal plane is 6 °, and all the other are identical with embodiment one.
embodiment three
Angle α between the bottom land of described seal groove and horizontal plane is 8 °, and all the other are identical with embodiment one.
Claims (4)
1. one kind adopts the minitype high-performance combination brake switch and proporting of linear compensation sealing configuration, comprise the combined type reversal valve group be located between oiling valve (1) and scavenger valve (6), each guiding valve of combined type reversal valve group is respectively equipped with the one-way valve (13) preventing fluid from flowing backwards; The valve body of described oiling valve (1), each guiding valve of combined type reversal valve group and scavenger valve (6) is provided with four corresponding attachment holes, four double threaded screws (7) are each passed through attachment hole corresponding on each valve body, coordinate fastening with nut (8), each guiding valve of oiling valve (1), combined type reversal valve group and scavenger valve (6) are connected as one; Described oiling valve (1), to be interconnected by being located at the parallel port (9) of side, middle bit port (10) and low-pressure channel (11) between each guiding valve of combined type reversal valve group and scavenger valve (6), to form complete hydraulic control oil circuit; It is characterized in that: the linear compensation sealing configuration that the hydraulic fluid port of the parallel port (9) of each valve body side, middle bit port (10) and low-pressure channel (11) all adopts seal groove and Sealing to form, described seal groove (18) is circular deep gouge, its central authorities communicate with hydraulic fluid port, the bottom land of seal groove is skewed, and the seal groove degree of depth is increased near groove side wall dimension linear by center; Described Sealing (17) is circular ring-type Sealing, and the sidewall of its excircle and described seal groove is close to.
2. a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration according to claim 1, is characterized in that: the angle α between the bottom land of described seal groove (18) and horizontal plane is 6 ° ~ 8 °.
3. a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration according to claim 1 and 2, is characterized in that: described combined type reversal valve group is made up of 1 ~ 10 guiding valve; Described guiding valve is O type function reversing valve (2), y-function selector valve (3), Type B function reversing valve (4) or N-type function reversing valve (5).
4. a kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration according to claim 1 and 2, is characterized in that: the overflow overload valve (12) being provided with regulable control pressure in described oiling valve (1).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420710223.2U CN204226324U (en) | 2014-11-24 | 2014-11-24 | A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420710223.2U CN204226324U (en) | 2014-11-24 | 2014-11-24 | A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration |
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| CN204226324U true CN204226324U (en) | 2015-03-25 |
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| CN201420710223.2U Active CN204226324U (en) | 2014-11-24 | 2014-11-24 | A kind of minitype high-performance combination brake switch and proporting adopting linear compensation sealing configuration |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105570223A (en) * | 2016-02-26 | 2016-05-11 | 龙工（上海）精工液压有限公司 | Sealing structure for preventing combination surfaces of chip type multi-way valves from leaking oil |
-
2014
- 2014-11-24 CN CN201420710223.2U patent/CN204226324U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105570223A (en) * | 2016-02-26 | 2016-05-11 | 龙工（上海）精工液压有限公司 | Sealing structure for preventing combination surfaces of chip type multi-way valves from leaking oil |
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