CN204253480U - Hydraulic multichannel valve core - Google Patents
Hydraulic multichannel valve core Download PDFInfo
- Publication number
- CN204253480U CN204253480U CN201420683008.8U CN201420683008U CN204253480U CN 204253480 U CN204253480 U CN 204253480U CN 201420683008 U CN201420683008 U CN 201420683008U CN 204253480 U CN204253480 U CN 204253480U
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- Prior art keywords
- throttling groove
- group
- oil
- valve core
- insert body
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Abstract
A kind of hydraulic multichannel valve core, comprises insert body, described insert body is respectively equipped with first segment chute group, second section chute group, the 3rd throttling groove group, the 4th throttling groove group and the 5th throttling groove group; The utility model by offering the throttling groove group of difformity, different openings length on insert body, thus ensures that the flow by spool is directly proportional to the overall process at spool travel; And effectively can avoid the impact phenomenon in spool opening and closing process and robust motion, thus improve micromanipulator performance and the precise positioning of working device of loader lifting or decline.
Description
Technical field
The utility model relates to a kind of core component of hydraulic multitandem valve, and particularly a kind of hydraulic multichannel valve core being applied to the engineering machinery such as loader, belongs to technical field of engineering machinery.
Background technique
Loader is a kind of based on the engineering machinery of loading and unloading material, and be mainly used in loaded material and short distance handling material, after discharging, hairpinning loads again.When loader pallet fork loads transporting cargo, need when putting goods to finely tune working device of loader, to adjust the height of goods.Therefore, the fine setting performance of loader to valve core of multiway valve using pallet fork to load transporting cargo has higher requirement.In order to increase work efficiency, operator often needs to promote Joystick fast, equipment is made to hoist rapidly according to the requirement of operator or drop to specified position, so just require that valve core of multiway valve has good speed adjusting performance: the flow of valve is directly proportional to the moving displacement amount of spool, valve open and close moment without impact.
In fixed dilivery hydraulic system, due to hydraulic system employing is metering pump, and the speed therefore controlling equipment rising and decline can only rely on the displacement amount of valve core movement.When spool opening hour, wish that the fluid flow passed through is also less; When valve core opening is large, wish that the fluid flow passed through is also larger.In prior art, although insert body also has throttling groove, but because the structural type of throttling groove is comparatively single, normally insert body is all semicircle or other shapes, and these throttling grooves offer only in order to slow down impact, therefore the displacement of spool and the flow of valve can not proportionally change, such operator opens the moment of spool, there is a larger opening area immediately in valve port, flow change rate can be caused excessive, cause hydraulic shock.And existing spool only moves to 2/3 or even 1/2 place often, valve core opening area has reached maximum.In this case, spool continues motion can not make valve core opening area increase, and thus the flow of valve can't change.That is, anyway operator promotes valve core movement, and the movement velocity of equipment all can not change, and make operator can control the scope of equipment movement velocity so very little, Here it is, and our said speed adjustable range is too small.The too small movement position causing the more difficult accurate control equipment of operator of speed adjustable range, reduces working efficiency.
Summary of the invention
Goal of the invention: the purpose of this utility model is to provide a kind of impact phenomenon, the robust motion that can effectively avoid in spool opening and closing process, and the hydraulic multichannel valve core improving working device of loader lifting or the micromanipulator performance declined and precise positioning.
Technological scheme: a kind of hydraulic multichannel valve core, comprises insert body, described insert body is respectively equipped with first segment chute group, second section chute group, the 3rd throttling groove group, the 4th throttling groove group and the 5th throttling groove group; Area of passage corresponding to first segment chute group, second section chute group, the 3rd throttling groove group, the 4th throttling groove group and the 5th throttling groove group is respectively S1, S2, S3, S4, S5, and effective displacement amount of insert body is L; Function relation then between area of passage and the effective displacement of insert body is: S1=K1 × L, S2=K2 × L, S3=K3 × L, S4=K4 × L, S5=K5 × L, and described K1, K2, K3, K4 and K5 are constant; During the large chamber oil return of loculus oil-feed: fluid is by the oil inlet quantity Q1 of area of passage S3, S4 co-controlling oil cylinder loculus of the 3rd throttling groove group and the 4th throttling groove group, then Q1=α S4/S3, the recirculating oil quantity Q2 in the large chamber of oil cylinder is controlled by the area of passage S1 of first segment chute group, relation between then Q2=β S1, loculus oil inlet quantity Q1 and large chamber recirculating oil quantity Q2 is Q1=γ Q2; During large chamber oil-feed loculus oil return: fluid controls the oil inlet quantity Q3 in the large chamber of oil cylinder by the area of passage S2 of second section chute group, then Q3=δ S2, the recirculating oil quantity Q4 of oil cylinder loculus is controlled by the area of passage S5 of the 5th throttling groove group, then Q4=ε S5, relation between large chamber oil inlet quantity Q3 and loculus recirculating oil quantity Q4 is Q3=γ Q4, and described α, β, γ, δ, ε are constant.
In order to the proportional change of flow of the displacement amount and valve that realize insert body, comprise base section chute and auxiliary throttling groove for first segment chute group described in first segment chute group, described base section chute and auxiliary throttling groove to be distributed on inside insert body on the shaft shoulder interlacedly.
Preference, described auxiliary throttling groove is leg-of-mutton throttling groove, and inside top adopts arc transition.
Preference, described auxiliary throttling groove is semicircle throttling groove.
Preference, described auxiliary throttling groove is inner end is semicircular long strip groove, and the degree of depth of described long strip groove is deepened gradually.
Preference, described auxiliary throttling groove is that two semicircle throttling grooves are formed by stacking.
Described second section chute group, the 3rd throttling groove group, the 4th throttling groove group are identical with the structure of first segment chute group with the structure of the 5th throttling groove group, but respective auxiliary throttling groove can combinationally use as required.
By simulation calculation and actual testing authentication, the present invention offers the base section chute groove of multiple combination and auxiliary throttling groove on valve core of multiway valve body, the auxiliary throttling groove different by orifice size, chock length is different combines, reach spool flow area and the proportional change of spool travel, and then adjustment enters flow, the pressure of valve port, improves the fretting performance of working device of loader and the precise positioning of equipment.
The present invention only need offer several auxiliary throttling grooves various in the first segment chute group of insert body, second section chute group, the 3rd throttling groove group, the 4th throttling groove group and the 5th throttling groove group, regulate orifice size by multiple auxiliary throttling groove shape and quantity and length etc., when equipment being promoted and declines, the change of flow is directly proportional to spool travel.
Beneficial effect: the utility model by offering the throttling groove group of difformity, different openings length on insert body, thus ensures that the flow by spool is directly proportional to the overall process at spool travel; And effectively can avoid the impact phenomenon in spool opening and closing process and robust motion, thus improve micromanipulator performance and the precise positioning of working device of loader lifting or decline.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model;
Fig. 2 is the utility model insert body first embodiment;
Fig. 3 is the utility model insert body second embodiment;
Fig. 4 is the utility model insert body the 3rd embodiment.
Embodiment
Below in conjunction with drawings and Examples, the utility model is described in further detail.
As shown in Figure 1, a kind of hydraulic multichannel valve core, comprises insert body 1, described insert body 1 is respectively equipped with first segment chute group 2, second section chute group the 3, the 3rd throttling groove group 4, the 4th throttling groove group 5 and the 5th throttling groove group 6; The area of passage of first segment chute group 2, second section chute group the 3, the 3rd throttling groove group 4, the 4th throttling groove group 5 and the 5th throttling groove group 6 correspondence is respectively S1, S2, S3, S4, S5, and effective displacement amount of insert body 1 is L; Then area of passage and the function relation of insert body 1 effectively between displacement are: S1=K1 × L, S2=K2 × L, S3=K3 × L, S4=K4 × L, S5=K5 × L, and described K1, K2, K3, K4 and K5 are constant; During the large chamber oil return of loculus oil-feed: fluid is by the oil inlet quantity Q1 of area of passage S3, S4 co-controlling oil cylinder loculus of the 3rd throttling groove group 4 and the 4th throttling groove group 5, then Q1=α S4/S3, the recirculating oil quantity Q2 in the large chamber of oil cylinder is controlled by the area of passage S1 of first segment chute group 2, relation between then Q2=β S1, loculus oil inlet quantity Q1 and large chamber recirculating oil quantity Q2 is Q1=γ Q2; During large chamber oil-feed loculus oil return: fluid controls the oil inlet quantity Q3 in the large chamber of oil cylinder by the area of passage S2 of second section chute group 3, then Q3=δ S2, the recirculating oil quantity Q4 of oil cylinder loculus is controlled by the area of passage S5 of the 5th throttling groove group 6, then Q4=ε S5, relation between large chamber oil inlet quantity Q3 and loculus recirculating oil quantity Q4 is Q3=γ Q4, and described α, β, γ, δ, ε are constant.
In order to the proportional change of flow of the displacement amount and valve that realize insert body 1, comprise base section chute 21 and auxiliary throttling groove 22 for first segment chute group 2 described in first segment chute group 2, described base section chute 21 and auxiliary throttling groove 22 to be distributed on inside insert body 1 on the shaft shoulder interlacedly.
Embodiment one
As shown in Figure 2, described auxiliary throttling groove 22 is leg-of-mutton throttling groove, and inside top adopts arc transition.
Embodiment two
As shown in Figure 3, described auxiliary throttling groove 22 is that two semicircle throttling grooves are formed by stacking.
Embodiment three
As shown in Figure 4, described auxiliary throttling groove 22 for inner end be semicircular long strip groove, the degree of depth of described long strip groove is deepened gradually.Described auxiliary throttling groove 22 also can be exactly directly semicircle throttling groove.
By simulation calculation and actual testing authentication, the present invention offers base section chute 21 and the auxiliary throttling groove 22 of multiple combination on valve core of multiway valve body 1, the auxiliary throttling groove 22 different by orifice size, chock length is different combines, reach spool flow area and the proportional change of spool travel, and then adjustment enters flow, the pressure of valve port, improves the fretting performance of working device of loader and the precise positioning of equipment.
The present invention only need offer several auxiliary throttling grooves 22 various in the first segment chute group 2 of insert body 1, second section chute group the 3, the 3rd throttling groove group 4, the 4th throttling groove group 5 and the 5th throttling groove group 6, regulate orifice size by multiple auxiliary throttling groove 22 shape and quantity and length etc., when equipment being promoted and declines, the change of flow is directly proportional to spool travel.Described second section chute group the 3, the 3rd throttling groove group 4, the 4th throttling groove group 5 are identical with the structure of first segment chute group 2 with the structure of the 5th throttling groove group 6, but respective auxiliary throttling groove can combinationally use as required.
In addition to the implementation, the utility model can also have other mode of executions, and all employings are equal to the technological scheme of replacement or equivalent transformation formation, all drop in the protection domain of the utility model requirement.
Claims (7)
1. a hydraulic multichannel valve core, comprise insert body (1), described insert body (1) is respectively equipped with first segment chute group (2), second section chute group (3), the 3rd throttling groove group (4), the 4th throttling groove group (5) and the 5th throttling groove group (6); It is characterized in that: area of passage corresponding to first segment chute group (2), second section chute group (3), the 3rd throttling groove group (4), the 4th throttling groove group (5) and the 5th throttling groove group (6) is respectively S1, S2, S3, S4, S5, and effective displacement amount of insert body (1) is L; Then area of passage and the function relation of insert body (1) effectively between displacement are: S1=K1 × L, S2=K2 × L, S3=K3 × L, S4=K4 × L, S5=K5 × L, and described K1, K2, K3, K4 and K5 are constant; During the large chamber oil return of loculus oil-feed: fluid is by the oil inlet quantity Q1 of area of passage S3, S4 co-controlling oil cylinder loculus of the 3rd throttling groove group (4) and the 4th throttling groove group (5), then Q1=α S4/S3, the recirculating oil quantity Q2 in the large chamber of oil cylinder is controlled by the area of passage S1 of first segment chute group (2), relation between then Q2=β S1, loculus oil inlet quantity Q1 and large chamber recirculating oil quantity Q2 is Q1=γ Q2; During large chamber oil-feed loculus oil return: fluid controls the oil inlet quantity Q3 in the large chamber of oil cylinder by the area of passage S2 of second section chute group (3), then Q3=δ S2, the recirculating oil quantity Q4 of oil cylinder loculus is controlled by the area of passage S5 of the 5th throttling groove group (6), then Q4=ε S5, relation between large chamber oil inlet quantity Q3 and loculus recirculating oil quantity Q4 is Q3=γ Q4, and described α, β, γ, δ, ε are constant.
2. hydraulic multichannel valve core as claimed in claim 1, it is characterized in that: described first segment chute group (2) comprises base section chute (21) and auxiliary throttling groove (22), described base section chute (21) and auxiliary throttling groove (22) are distributed on the shaft shoulder of insert body (1) inner side interlacedly.
3. hydraulic multichannel valve core as claimed in claim 2, is characterized in that: described auxiliary throttling groove (22) is leg-of-mutton throttling groove, and inside top adopts arc transition.
4. hydraulic multichannel valve core as claimed in claim 2, is characterized in that: described auxiliary throttling groove (22) is semicircle throttling groove.
5. hydraulic multichannel valve core as claimed in claim 2, is characterized in that: described auxiliary throttling groove (22) for inner end be semicircular long strip groove, the degree of depth of described long strip groove is deepened gradually.
6. hydraulic multichannel valve core as claimed in claim 2, is characterized in that: described auxiliary throttling groove (22) is that two semicircle throttling grooves are formed by stacking.
7. the hydraulic multichannel valve core according to any one of claim 2-6, is characterized in that: described second section chute group (3), the 3rd throttling groove group (4), the 4th throttling groove group (5) are identical with the structure of first segment chute group (2) with the structure of the 5th throttling groove group (6).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420683008.8U CN204253480U (en) | 2014-11-14 | 2014-11-14 | Hydraulic multichannel valve core |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420683008.8U CN204253480U (en) | 2014-11-14 | 2014-11-14 | Hydraulic multichannel valve core |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204253480U true CN204253480U (en) | 2015-04-08 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420683008.8U Withdrawn - After Issue CN204253480U (en) | 2014-11-14 | 2014-11-14 | Hydraulic multichannel valve core |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204253480U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373402A (en) * | 2014-11-14 | 2015-02-25 | 江苏柳工机械有限公司 | Valve element of hydraulic multi-way valve |
-
2014
- 2014-11-14 CN CN201420683008.8U patent/CN204253480U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104373402A (en) * | 2014-11-14 | 2015-02-25 | 江苏柳工机械有限公司 | Valve element of hydraulic multi-way valve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150408 Effective date of abandoning: 20160706 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |