CN111963735A

CN111963735A - Threaded cartridge type balance valve

Info

Publication number: CN111963735A
Application number: CN202010794627.4A
Authority: CN
Inventors: 彭锋; 罗占涛; 陶小好
Original assignee: Zhejiang Huayi Precision Machinery Co ltd
Current assignee: Zhejiang Huaju Hydraulic Technology Co.,Ltd.
Priority date: 2020-08-10
Filing date: 2020-08-10
Publication date: 2020-11-20

Abstract

The invention relates to a thread cartridge type balance valve, which comprises a valve sleeve and a valve core, wherein the valve sleeve is provided with a valve cavity, a first cavity and a second cavity, and the valve core is slidably arranged in the valve cavity; the first chamber and the second chamber are respectively positioned at two ends of the valve sleeve; the outer wall of the valve pocket is provided with a first oil port, a second oil port, a third oil port, a fourth oil port, a first throttling hole, a second throttling hole and a throttling channel which are communicated with the valve pocket, the first oil port is communicated with the first cavity, the second oil port is communicated with the first throttling hole and the throttling channel respectively, the third oil port is communicated with the second throttling hole and the throttling channel respectively, and the fourth oil port is communicated with the second cavity. The invention has the advantages that: simple structure, can throttle the backward flow to reduce jolting and shorten braking distance.

Description

Threaded cartridge type balance valve

Technical Field

The invention relates to the technical field of hydraulic valves, in particular to a threaded cartridge type balance valve.

Background

The balancing valve is a key element in the hydraulic circuit. The prior scissor operation platform vehicle is driven by a multi-purpose hydraulic motor, when operation needs high speed downhill, the flow rate required by the hydraulic motor is larger than the inlet flow rate of a pump due to self weight and inertia force, the inlet pressure of the hydraulic motor is reduced and is lower than the opening pressure of a brake, so that the brake is closed in a short time, and the scissor operation platform vehicle generates bump feeling; further, when a sudden stop is required on a downhill, a large braking distance is required to stop the hydraulic motor by the brake alone due to a large inertia force.

Disclosure of Invention

In view of the above, it is desirable to provide a cartridge type balance valve which can throttle backflow, reduce jounce and braking distance, and has a simple structure.

The invention provides a thread cartridge type balance valve which comprises a valve sleeve and a valve core, wherein the valve sleeve is provided with a valve cavity, a first cavity and a second cavity, and the valve core is slidably arranged in the valve cavity; the first chamber and the second chamber are respectively positioned at two ends of the valve sleeve;

the outer wall of the valve pocket is provided with a first oil port, a second oil port, a third oil port, a fourth oil port, a first throttling hole, a second throttling hole and a throttling channel, the first oil port is communicated with the first chamber, the second oil port is respectively communicated with the first throttling hole and the throttling channel, the third oil port is respectively communicated with the second throttling hole and the throttling channel, and the fourth oil port is communicated with the second chamber;

when the pressure of the first chamber is the same as that of the second chamber, the valve core is pushed to slide to the central position of the valve cavity, and a part of hydraulic oil returns from the second oil port to the first oil port through the first throttle hole; a part of hydraulic oil flows back to the second oil port from the third oil port through the throttling channel; or, a part of hydraulic oil returns from the third oil port to the fourth oil port through the second throttle hole; and a part of hydraulic oil flows back to the third oil port from the second oil port through the throttling channel.

In the application, when the engine runs down a slope or stops suddenly, if the first chamber is connected with the outlet of the pump body, the pressure of the first chamber is reduced, the valve core tends to slide to the central position of the valve cavity, and a part of hydraulic oil at the outlet of the hydraulic motor returns to the oil tank through the second throttling hole to generate large throttling; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel, and the oil quantity at the inlet of the hydraulic motor is supplemented; similarly, if the second chamber is connected with the outlet of the pump body, a part of hydraulic oil at the outlet of the hydraulic motor returns to the oil tank through the first throttling hole, and large throttling is generated; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel, and the oil quantity at the inlet of the hydraulic motor is supplemented, so that the conditions of bumping and overlong braking distance caused by stalling or air suction of the hydraulic motor are avoided.

In one embodiment, the throttling channel comprises a third throttling hole and a fourth throttling hole, the valve core is provided with a first oil groove, the third throttling hole is communicated with the second oil port, and the fourth throttling hole is communicated with the third oil port; when the valve core slides to the center position of the valve cavity, the first oil groove is communicated with the third throttling hole and the fourth throttling hole respectively.

So set up, when the pressure of first cavity and second cavity is the same, the case slides to the central point of valve pocket and puts, first oil groove and third orifice and fourth orifice intercommunication, and hydraulic oil can flow back through throttle passage to make up the not enough of hydraulic motor entry flow, alleviate jolting, avoid hydraulic motor to inhale the sky and produce the problem of abnormal sound and braking distance overlength.

In one embodiment, the valve core is further provided with a second oil groove, a third oil groove, a fourth oil groove and a fifth oil groove; the second oil groove is communicated with the first oil port, and the fifth oil groove is communicated with the fourth oil port; the second oil groove is selectively communicated with the first throttling hole and/or the second oil port along with the movement of the valve core; the third oil groove can be communicated with the second oil port; the fourth oil groove can be communicated with the third oil port; the fifth oil groove selectively communicates with the third oil port and/or the second orifice.

So set up, at the in-process that the case removed, be convenient for the storage and the circulation of the interior hydraulic oil of screw thread cartridge formula balanced valve.

In one embodiment, a fifth orifice and a sixth orifice are further formed in the outer wall of the valve sleeve, and the fifth orifice is communicated with the first chamber and the first oil port respectively; the sixth throttle hole is communicated with the second chamber and the fourth oil port respectively;

when hydraulic oil flows in from the first oil port and flows to the first chamber through the fifth throttling hole, the valve core slides rightwards; when hydraulic oil flows in from the fourth oil port and flows to the second chamber through the sixth orifice, the valve element slides to the left.

It will be appreciated that when hydraulic oil flows to the first chamber through the fifth orifice, a greater pressure will be generated to urge the spool to slide to the right, and when hydraulic oil flows to the second chamber through the sixth orifice, a greater pressure will be generated to urge the spool to slide to the left.

In one embodiment, the valve core comprises a first part and a second part, the first part is provided with a first channel along the axial direction of the valve core, and the second part is provided with a fourth channel;

a second channel and a third channel are formed in the first part along the radial direction of the valve core, the first channel is respectively communicated with the second channel and the third channel, the second channel is communicated with the second oil groove, and the third channel is communicated with the third oil groove; fifth passageway and sixth passageway have been seted up to the second part, the fourth passageway respectively with the fifth passageway sixth passageway intercommunication, the fifth passageway with the fourth oil groove intercommunication, the sixth passageway with the fifth oil groove intercommunication.

So set up, when normal operating, hydraulic oil can be quick switching between the pump body and hydraulic motor, and case formula simple structure as an organic whole, and the hydraulic oil switching-over of being convenient for flows.

In one embodiment, the threaded cartridge balance valve further comprises a first sealing element and a second sealing element, the first sealing element is arranged in the first channel, and the first sealing element is positioned between the second channel and the first chamber and is in sealing contact with the inner wall of the first channel; the second seal is disposed in the second channel, and the second seal is located between the sixth channel and the second chamber and is in sealing contact with an inner wall of the second channel.

It will be appreciated that the first seal separates the first chamber from the second and third passages such that hydraulic oil cannot flow into the first chamber through the second and third passages; the second seal separates the second chamber from the fifth passage and the sixth passage, so that hydraulic oil cannot flow into the second chamber through the fifth passage and the sixth passage.

In one embodiment, when the pressure of the second chamber is higher than that of the first chamber, the valve element moves to the left, hydraulic oil enters the hydraulic motor inlet through the fourth oil port, the fifth oil groove and the third oil port in sequence and flows into the second oil port through the hydraulic motor outlet, and hydraulic oil of the second oil port flows into the second oil groove through the third oil groove, the third passage, the first passage and the second passage and enters the first oil port to flow back to the oil tank;

when the pressure of the first chamber is larger than that of the second chamber, the valve core moves to the right, hydraulic oil enters the hydraulic motor inlet through the first oil port, the second oil groove and the second oil port in sequence and flows into the third oil port through the hydraulic motor outlet, and the hydraulic oil of the third oil port flows into the fifth oil groove through the fourth oil groove, the fifth channel, the fourth channel and the sixth channel and flows into the fourth oil port to flow back to the oil tank.

So set up, through first passageway, fourth passageway respectively with the sealed cooperation of first sealing member, second sealing member, fixed the circulation route of hydraulic oil, when the in-process that the case removed in the valve chamber, can realize the switching-over circulation of hydraulic oil.

In one embodiment, the threaded cartridge type balance valve further comprises a valve seat, a third sealing element, a first elastic element and a second elastic element, wherein the valve seat is provided with a notch, and one end of the valve sleeve extends into and is installed in the notch in a sealing mode; the notch, the inner wall of the valve sleeve and one end of the valve core close to the valve seat form the first chamber, the first elastic piece is arranged in the first chamber, and two ends of the first elastic piece respectively abut against the valve seat and the valve core;

the third sealing element is blocked at one end, far away from the valve seat, of the valve sleeve, the third sealing element, the inner wall of the valve sleeve and one end, far away from the valve seat, of the valve core form the second chamber, the second elastic element is arranged in the second chamber, and two ends of the second elastic element are respectively abutted against the valve core and the third sealing element.

So set up, when downhill path or suddenly stopped, the elastic component at case both ends produced the same size pressure, made the case remove to the central point of valve pocket and put, this moment screw thread cartridge formula balance valve only need overcome the pretightning force of elastic component can, can reduce the pressure loss, more energy-conserving.

In one embodiment, a first step is provided at an end of the valve seat adjacent to the notch, and a protrusion is provided on the valve sleeve, and the protrusion abuts against the first step when the end of the valve sleeve is inserted into and installed in the notch.

So set up, avoid the valve barrel to stretch into the entrance too deeply, strengthen the fixed of valve barrel simultaneously.

In one embodiment, the threaded cartridge type balance valve further comprises a first sealing ring, a second sealing ring and a third sealing ring which are sleeved on the outer wall of the valve sleeve, and the fifth throttling hole and the first oil port are sequentially distributed between the protrusion and the first sealing ring; the first throttling hole, the second oil port and the third throttling hole are sequentially distributed between the first sealing ring and the second sealing ring; the fourth throttling hole, the third oil port and the second throttling hole are sequentially distributed between the second sealing ring and the third sealing ring; and a fourth oil port and a sixth throttling hole are sequentially distributed between the third sealing ring and the third sealing element.

So set up, rationally set up the position of each hydraulic fluid port and orifice, make and connect the general pipeline of hydraulic oil stream small in quantity, occupation space is little, and the hydraulic oil that flows through the throttle passageway can be quick flows back to the oil mass of supplementary hydraulic motor entry lacks.

Compared with the prior art, according to the threaded cartridge type balance valve provided by the invention, when the valve goes down a slope or stops suddenly, the pressure of the first chamber is the same as that of the second chamber, so that the valve core can slide to the central position of the valve cavity, and a part of hydraulic oil at the outlet of the hydraulic motor returns to an oil tank through the second throttling hole to generate large throttling; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel, and the oil quantity at the inlet of the hydraulic motor is supplemented; or, a part of hydraulic oil at the outlet of the hydraulic motor returns to the oil tank through the first throttling hole to generate larger throttling; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel, and the oil quantity at the inlet of the hydraulic motor is supplemented, so that the conditions of bumping and overlong braking distance caused by stalling or air suction of the hydraulic motor are avoided.

Drawings

FIG. 1 is a schematic view of a threaded cartridge type balance valve provided by the invention in a valve cavity at a neutral position;

FIG. 2 is a schematic diagram of the threaded cartridge type balance valve provided by the invention in a valve cavity at a neutral position;

FIG. 3 is a schematic view of the threaded cartridge type balance valve provided by the present invention at the left position of the valve cavity;

FIG. 4 is a schematic diagram of the threaded cartridge type balance valve provided by the invention at the left position of the valve cavity;

FIG. 5 is a schematic view of the threaded cartridge type balance valve provided by the present invention at the right position of the valve cavity;

fig. 6 is a schematic diagram of the threaded cartridge type balance valve provided by the invention at the right position of the valve cavity.

In the figure, 100, a threaded cartridge type balance valve; 10. a valve housing; 11. a valve cavity; 12a, a first oil port; 12b and a second oil port; 12c, a third oil port; 12d, a fourth oil port; 13a, a first orifice; 13b, a second orifice; 13. a throttling channel; 13c, a third orifice; 13d, a fourth orifice; 13e, a fifth orifice; 13f, a sixth orifice; 14. an external thread; 15. a protrusion; 16a, a first annular groove; 16b, a second annular groove; 16c, a third annular groove; 17. a first chamber; 18. a second chamber; 20. a valve core; 21a, a first oil groove; 21b, a second oil groove; 21c, a third oil groove; 21d, a fourth oil groove; 21e, a fifth oil groove; 22. a first portion; 221. a first channel; 222. a second channel; 223. a third channel; 23. a second portion; 231. a fourth channel; 232. a fifth channel; 233. a sixth channel; 24. a second step; 25. a third step; 30. a first seal member; 40. a second seal member; 50. a valve seat; 51. a notch; 52. an internal thread; 53. a first step; 60. a third seal member; 70. a first elastic member; 80. a second elastic member; 90. a first seal ring; 91. a second seal ring; 92. and a third sealing ring.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.

It will be understood that when an element is referred to as being "mounted on" another element, it can be directly mounted on the other element or intervening elements may also be present. When a component is referred to as being "disposed on" another component, it can be directly on the other component or intervening components may also be present. When an element is referred to as being "secured to" another element, it can be directly secured to the other element or intervening elements may also be present.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "or/and" includes any and all combinations of one or more of the associated listed items.

As shown in fig. 1 to 6, the present invention provides a threaded cartridge type balance valve 100, which is applied to a hydraulic load-bearing system, a load control system, etc., for adjusting pressure and flow balance in each system, and the threaded cartridge type balance valve 100 is applied to the hydraulic load-bearing system, the load control system, etc. In this embodiment, the threaded cartridge type balance valve 100 is mainly connected to a hydraulic valve block on a scissor work platform truck, and is used for adjusting the flow of hydraulic oil required by a hydraulic motor, so as to reduce the jolt of the scissor truck and the braking distance of the hydraulic motor.

Further, in the present application, the cartridge type balance valve 100 has three states including a neutral position, a left shift, and a right shift, which can be automatically switched to various states according to the pressure and flow demand of the hydraulic motor.

Specifically, referring to fig. 1-2, the threaded cartridge balance valve 100 includes a valve housing 10 and a valve core 20, the valve housing 10 has a valve cavity 11, a first chamber 17 and a second chamber 18, and the valve core 20 is slidably mounted in the valve cavity 11; the first chamber 17 and the second chamber 18 are respectively located at both ends of the valve housing 10; the outer wall of the valve pocket 10 is provided with a first oil port 12a, a second oil port 12b, a third oil port 12c, a fourth oil port 12d, a first throttle hole 13a, a second throttle hole 13b and a throttle passage 13 which are communicated with the valve cavity 11, the first oil port 12a is communicated with the first chamber 17, the second oil port 12b is communicated with the first throttle hole 13a and the throttle passage 13 respectively, the third oil port 12c is communicated with the second throttle hole 13b and the throttle passage 13 respectively, and the fourth oil port 12d is communicated with the second chamber 18;

when the pump body entry and first hydraulic fluid port 12a intercommunication, the pump body export communicates with fourth hydraulic fluid port 12d, and the hydraulic motor entry communicates with second hydraulic fluid port 12b, and the hydraulic motor export communicates with third hydraulic fluid port 12 c: when the scissor-fork work platform truck goes down a slope or stops suddenly, the pressure of the second chamber 18 is reduced (the pressure of the pump body outlet is reduced), so that the pressure of the first chamber 17 is the same as that of the second chamber 18, the valve core 20 is pushed to slide to the center of the valve cavity 11, and a part of hydraulic oil returns to the first oil port 12a from the second oil port 12b through the first throttling hole 13 a; a part of the hydraulic oil flows back to the second oil port 12b from the third oil port 12c through the throttling passage 13;

when the pump body inlet communicates with the fourth oil port 12d, the pump body outlet communicates with the first oil port 12a, the hydraulic motor inlet communicates with the third oil port 12c, and the hydraulic motor outlet communicates with the second oil port 12 b: when the scissor-fork work platform truck goes down a slope or stops suddenly, the pressure of the first chamber 17 is reduced (the pressure of the pump body outlet is reduced), so that the pressure of the first chamber 17 is the same as that of the second chamber 18, the valve core 20 is pushed to slide to the center of the valve cavity 11, and a part of hydraulic oil returns from the third oil port 12c to the fourth oil port 12d through the second throttling hole 13 b; a part of the hydraulic oil is returned from the second port 12b to the third port 12c through the orifice passage 13.

Of course, when the scissors platform vehicle goes down a slope or stops suddenly, the pressure in the second chamber 18 will decrease (the pressure at the pump body outlet will decrease), and at this time, the pressures in the first chamber 17 and the second chamber 18 may also be approximately the same, so as to push the valve core 20 to slide to the center of the valve cavity 11.

It can be understood that, by providing the throttling channel 13, when the scissors operating platform vehicle runs down a slope or stops suddenly, due to self-weight and inertia force, the pressure at the outlet of the pump body is reduced, the flow rate required by the inlet of the hydraulic motor is greater than the flow rate at the inlet of the pump body, so that the pressures of the first chamber 17 and the second chamber 18 are the same, and the valve core 20 can slide to the central position of the valve cavity 11 (i.e. the threaded cartridge type balance valve 100 is in a neutral state), and in this state, the hydraulic oil at the outlet of the hydraulic motor can return to the oil tank through the second throttling hole 13b, so as to generate a large throttling; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel 13, or the hydraulic oil at the outlet of the hydraulic motor can return to an oil tank through the first throttling hole 13a, so that large throttling is generated; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor flows back to the inlet of the hydraulic motor through the throttling channel 13, and the oil quantity at the inlet of the hydraulic motor is supplemented, so that the conditions of jolt and overlong braking distance caused by stalling or suction of the hydraulic motor are avoided.

Preferably, in the axial direction of the valve housing 10, the first port 12a, the second port 12b, the third port 12c, and the fourth port 12d are sequentially disposed on the valve housing 10, and the first orifice 13a, the throttle passage 13, and the second orifice 13b are sequentially disposed on the valve housing 10; when the scissor-fork work platform truck goes down a slope or stops suddenly, hydraulic oil directly flows back to the third oil port 12c from the second oil port 12b through the throttling channel 13 or directly flows back to the second oil port 12b from the third oil port 12c through the throttling channel 13, so that the inlet flow of the hydraulic motor is returned and supplemented with the hydraulic oil; the first orifice 13a is provided between the first port 12a and the second port 12b, and the second orifice 13b is provided between the third port 12c and the fourth port 12 d. It can be understood that, by reasonably setting the positions of the oil ports and the throttle holes, the number of pipelines for connecting hydraulic oil flows is the minimum, the oil path of the hydraulic oil is the shortest, the volume of the threaded cartridge type balance valve 100 is effectively reduced, and the structure of the threaded cartridge type balance valve 100 is more compact.

Furthermore, a fifth orifice 13e and a sixth orifice 13f are further opened on the outer wall of the valve sleeve 10, and the fifth orifice 13e is respectively communicated with the first chamber 17 and the first oil port 12 a; the sixth orifice 13f communicates with the second chamber 18 and the fourth port 12d, respectively; as shown in fig. 3, when the hydraulic oil flows from the fourth port 12d through the sixth orifice 13f and into the second valve chamber 11, a large pressure is generated to push the valve spool 20 to move to the left (i.e., the threaded cartridge type balance valve 100 is in a left movement state); as shown in fig. 5, when the hydraulic oil flows from the first port 12a through the fifth orifice 13e into the second chamber 18, a large pressure is generated to push the valve spool 20 to move rightward (i.e., the threaded cartridge type balance valve 100 is in a rightward movement state). It should be noted that in the present application, the relative positions of the left, right and center are based on the left, right and center of the valve sleeve 10 in the drawings.

As shown in fig. 1, the orifice passage 13 includes a third orifice 13c and a fourth orifice 13d, the valve core 20 has a first oil groove 21a, the third orifice 13c communicates with the second port 12b, and the fourth orifice 13d communicates with the third port 12 c; when the vehicle runs downhill or stops suddenly, the pressure in the first chamber 17 is the same as that in the second chamber 18, so that the valve core 20 slides to the center of the valve cavity 11, the first oil groove 21a is communicated with the third orifice 13c and the fourth orifice 13d, and hydraulic oil can flow back through the orifice passage 13, so that the shortage of inlet flow of the hydraulic motor is compensated, the jolt is relieved, abnormal sound caused by air suction of the hydraulic motor is avoided, and the braking distance is shortened.

As shown in fig. 1 to 6, the valve core 20 is further provided with a second oil groove 21b, a third oil groove 21c, a fourth oil groove 21d, and a fifth oil groove 21 e; the second oil groove 21b is communicated with the first oil port 12a, and the fifth oil groove 21e is communicated with the fourth oil port 12 d; the second oil groove 21b selectively communicates with the first orifice 13a and/or the second oil port 12b as the spool 20 moves; the third oil groove 21c can communicate with the second oil port 12 b; the fourth oil groove 21d can communicate with the third oil port 12 c; the fifth oil groove 21e selectively communicates with the third port 12c and/or the second orifice 13 b.

As shown in fig. 3 to 4, when the pressure of the second chamber 18 is greater than that of the first chamber 17, the valve spool 20 moves to the left end (the left end of the valve housing 10), the second oil groove 21b communicates with the first oil port 12a, and the third oil groove 21c communicates with the second oil port 12 b; the fifth oil groove 21e communicates with the third port 12c, the second orifice 13b, and the fourth port 12 d; the hydraulic oil flows from the fourth oil port 12d through the fifth oil groove 21e into the third oil port 12c, and thus into the hydraulic motor inlet, from the hydraulic motor outlet into the second oil port 12b, and into the second oil groove 21b into the first oil port 12a, and back to the oil tank.

As shown in fig. 5 to 6, when the pressure of the first chamber 17 is greater than that of the second chamber 18, the valve spool 20 moves to the right end (the right end of the valve housing 10), the fifth oil groove 21e communicates with the fourth oil port 12d, and the fourth oil groove 21d communicates with the third oil port 12 c; the second oil groove 21b communicates with the first port 12a, the first orifice 13a, and the second port 12 b; the hydraulic oil flows from the first oil port 12a through the second oil groove 21b into the second oil port 12b, and thus into the hydraulic motor inlet, from the hydraulic motor outlet into the third oil port 12c, and into the fifth oil groove 21e into the fourth oil port 12d, and back to the oil tank.

As shown in fig. 1, the valve core 20 includes a first portion 22 and a second portion 23, and along the axial direction of the valve core 20, the first portion 22 is opened with a first channel 221, and the second portion 23 is opened with a fourth channel 231; along the radial direction of the valve core 20, the first part 22 is provided with a second channel 222 and a third channel 223, the first channel 221 is respectively communicated with the second channel 222 and the third channel 223, the second channel 222 is communicated with the second oil groove 21b, and the third channel 223 is communicated with the third oil groove 21 c; the second portion 23 is provided with a fifth passage 232 and a sixth passage 233, the fourth passage 231 is respectively communicated with the fifth passage 232 and the sixth passage 233, the fifth passage 232 is communicated with the fourth oil groove 21d, and the sixth passage 233 is communicated with the fifth oil groove 21 e. Specifically, the second passage 222, the third passage 223, the fifth passage 232, and the sixth passage 233 are provided on the spool 20 in order from left (near the first chamber 17) to right (near the second chamber 18).

When the pressure of the second chamber 18 is higher than that of the first chamber 17, the valve core 20 moves to the left (i.e., the threaded cartridge type balance valve 100 is in a left-moving state), and the hydraulic oil flowing into the second oil port 12b through the outlet of the hydraulic motor flows into the second oil tank 21b through the third oil groove 21c, the third passage 223, the first passage 221, the second passage 222, enters the first oil port 12a and flows back to the oil tank;

when the pressure in the first chamber 17 is higher than that in the second chamber 18, the valve core 20 moves to the right (i.e., the threaded cartridge type balance valve 100 is in the state of moving to the right), and the hydraulic oil flowing into the third port 12c through the outlet of the hydraulic motor flows into the fifth oil groove 21e through the fourth oil groove 21d, the fifth passage 232, the fourth passage 231, and the sixth passage 233, and enters the fourth port 12d to flow back to the oil tank.

Specifically, the threaded cartridge balance valve 100 further comprises a first sealing member 30 and a second sealing member 40, the first sealing member 30 is disposed in the first passage 221, and the first sealing member 30 is located between the second passage 222 and the first chamber 17 and is in sealing contact with the inner wall of the first passage 221; the first seal 30 separates the first chamber 17 from the second passage 222 and the third passage 223, so that hydraulic oil cannot flow into the first chamber 17 through the second passage 222 and the third passage 223;

the second seal 40 is disposed in the second channel 222, and the second seal 40 is located between the sixth channel 233 and the second chamber 18 and is in sealing contact with the inner wall of the second channel 222; the second seal 40 separates the second chamber 18 from the fifth passage 232 and the sixth passage 233, so that hydraulic oil cannot flow into the second chamber 18 through the fifth passage 232 and the sixth passage 233. Therefore, the flow direction of the hydraulic oil is controlled, and the hydraulic oil can freely flow in a reversing way in the process that the valve core 20 moves in the valve cavity 11.

In the present embodiment, the first sealing element 30 and the second sealing element 40 are both plugs, but the first sealing element 30 and the second sealing element 40 may also be other components that perform the same sealing function, such as silicone sealing plugs.

As shown in fig. 3-4, when the pressure of the second chamber 18 is greater than that of the first chamber 17, the valve core 20 moves left (i.e., the threaded cartridge type balance valve 100 is in a left moving state), hydraulic oil enters the hydraulic motor inlet through the fourth oil port 12d, the fifth oil groove 21e and the third oil port 12c in sequence and flows into the second oil port 12b through the hydraulic motor outlet, and hydraulic oil in the second oil port 12b flows into the second oil groove 21b through the third oil groove 21c, the third passage 223, the first passage 221 and the second passage 222 and enters the first oil port 12a to flow back to the oil tank;

as shown in fig. 5-6, when the pressure of the first chamber 17 is greater than that of the second chamber 18, the valve core 20 moves to the right (i.e., the threaded cartridge type balance valve 100 is in a right-moving state), hydraulic oil enters the hydraulic motor inlet through the first oil port 12a, the second oil groove 21b and the second oil port 12b in sequence, and flows into the third oil port 12c through the hydraulic motor outlet, and hydraulic oil in the third oil port 12c flows into the fifth oil groove 21e through the fourth oil groove 21d, the fifth passage 232, the fourth passage 231 and the sixth passage 233, and flows into the fourth oil port 12d to flow back to the oil tank.

As shown in fig. 1, the threaded cartridge type balance valve 100 further includes a valve seat 50, the valve seat 50 is opened with a notch 51, and one end of the valve housing 10 is inserted and mounted in the notch 51. Specifically, the inner wall of the notch 51 is provided with an internal thread 52, and the outer wall of one end of the valve sleeve 10 extending into the notch 51 is provided with an external thread 14, so that the valve seat 50 and the valve sleeve 10 are tightly fixed; a first step 53 is arranged at one end, close to the notch 51, of the valve seat 50, a protrusion 15 is arranged on the valve sleeve 10, when one end of the valve sleeve 10 extends into and is installed in the notch 51, the protrusion 15 abuts against the first step 53, and the situation that the valve sleeve 10 extends into the notch 51 too deeply when the valve sleeve 10 is in threaded fit with the notch 51 is avoided; at the same time, a positioning of the valve housing 10 is formed, so that the installation of the valve housing 10 is more stable.

In the specification, in the present application, the valve element 20 moves to the left, that is, the valve element 20 moves to a direction close to the valve seat 50; the valve element 20 moves to the right, i.e., the valve element 20 moves away from the valve seat 50. The valve core 20 is in a neutral position, i.e., the valve core 20 is in a center position of the valve housing 10, i.e., the center of the valve core 20 coincides with the center of the valve housing 10.

Further, as shown in fig. 1, the threaded cartridge type balance valve 100 further includes a third sealing member 60, a first elastic member 70 and a second elastic member 80, the third sealing member 60 is sealed at one end of the valve housing 10 away from the valve seat 50, the notch 51, the inner wall of the valve housing 10 and one end of the valve core 20 close to the valve seat 50 form a first chamber 17, the first elastic member 70 is disposed in the first chamber 17, and two ends of the first elastic member 70 respectively abut against the valve seat 50 and the valve core 20; the third sealing member 60 forms a second chamber 18 with the inner wall of the valve housing 10 and one end of the valve core 20 away from the valve seat 50, the second elastic member 80 is disposed in the second chamber 18, and two ends of the second elastic member 80 respectively abut against the valve core 20 and the third sealing member 60.

When the valve is going downhill or stopped suddenly, the elastic members at the two ends of the valve core 20 generate the same pressure, and the valve core 20 moves to the central position of the valve cavity 11, so that the threaded cartridge type balance valve 100 only needs to overcome the pretightening force of the first elastic member 70 and the second elastic member 80, thereby reducing the pressure loss and saving more energy. Of course, when the scissors platform truck goes down a slope or stops suddenly, the pressure generated by the elastic members at the two ends of the spool 20 may also be approximately the same, so as to push the spool 20 to slide to the center of the valve cavity 11.

Preferably, one end of the valve core 20 close to the valve seat 50 is provided with a second step 24, and one end of the valve core 20 far away from the valve seat 50 is provided with a third step 25; one end of the first elastic element 70 abuts against the notch 51, and the other end abuts against the second step 24; the second elastic member 80 abuts against the third step 25 at one end and the third sealing member 60 at the other end.

In the present embodiment, the third sealing element 60 is a plug, but the third sealing element 60 may also be other components that perform the same sealing function, such as a silicone sealing plug.

As shown in fig. 1, the threaded cartridge balance valve 100 further includes a first sealing ring 90, a second sealing ring 91, and a third sealing ring 92, a first annular groove 16a, a second annular groove 16b, and a third annular groove 16c are circumferentially disposed on an outer wall of the valve housing 10, the first sealing ring 90 is sleeved in the first annular groove 16a, the second sealing ring 91 is sleeved in the second annular groove 16b, and the third sealing ring 92 is sleeved in the third annular groove 16c, so as to prevent leakage of hydraulic oil. Meanwhile, a first orifice 13a, a second oil port 12b and a third orifice 13c are sequentially arranged between the first sealing ring 90 and the second sealing ring 91; a fourth orifice 13d, a third port 12c, and a second orifice 13b are arranged in this order between the second seal ring 91 and the third seal ring 92; a fifth orifice 13e and a first oil port 12a are sequentially arranged between the bulge 15 and the first sealing ring 90; a fourth port 12d and a sixth orifice 13f are arranged in this order between the third seal ring 92 and the third seal 60.

In the normal operation of the threaded cartridge type balance valve 100 provided by the invention, hydraulic oil enters the threaded cartridge type balance valve 100 from the oil tank, then enters the hydraulic motor inlet, flows into the threaded cartridge type balance valve 100 from the hydraulic motor outlet, and returns to the oil tank from the threaded cartridge type balance valve 100, and the operation is repeated in such a way, so that the hydraulic motor operates normally. At this time, the valve core 20 is pushed to move left or right according to the pressure difference between the first elastic member 70 and the second elastic member 80, so that the flow is reversed.

When the hydraulic oil flows into the valve chamber 11 from the fourth oil port 12d through the sixth orifice 13f, the pressure of the second elastic member 80 is greater than that of the first elastic member 70, so as to push the valve element 20 to move leftward (i.e., in a direction close to the valve seat 50), the hydraulic oil sequentially flows into the inlet of the hydraulic motor through the fourth oil port 12d, the fifth oil groove 21e, and the third oil port 12c, and flows into the second oil port 12b through the outlet of the hydraulic motor, and the hydraulic oil of the second oil port 12b flows into the second oil groove 21b through the third oil groove 21c, the third passage 223, the first passage 221, the second passage 222, and flows into the first oil port 12a to flow back to the oil tank; when the hydraulic oil flows into the valve chamber 11 from the first oil port 12a through the fifth orifice 13e, the pressure of the first elastic member 70 is greater than that of the second elastic member 80, so as to push the valve element 20 to move rightward (i.e., away from the valve seat 50), the hydraulic oil sequentially flows through the first oil port 12a, the second oil groove 21b, the second oil port 12b, enters the hydraulic motor inlet, and flows into the third oil port 12c through the hydraulic motor outlet, and the hydraulic oil of the third oil port 12c flows into the fifth oil groove 21e through the fourth oil groove 21d, the fifth passage 232, the fourth passage 231, and the sixth passage 233, and flows into the fourth oil port 12d to flow back to the oil tank, thereby forming a complete circulation of the hydraulic oil.

When the hydraulic motor is in a downhill state or needs to stop, the pump body flow cannot meet the speed of the hydraulic motor, so that the pressure at the outlet of the pump body is reduced, the pressure of the first elastic element 70 is the same as that of the second elastic element 80, the valve core 20 slides to the center position of the valve cavity 11, at the moment, the hydraulic motor generates large throttling, meanwhile, a part of hydraulic oil flows back to the inlet of the hydraulic motor, and the flow at the inlet of the hydraulic motor is supplemented, so that the stalling or the suction of the hydraulic motor is relieved.

When the first oil port 12a and the fourth oil port 12d are respectively connected with the pump body inlet and the pump body outlet, and the second oil port 12b and the third oil port 12c are respectively connected with the hydraulic motor inlet and the hydraulic motor outlet; the hydraulic oil in the second oil port 12b is returned through the first orifice 13a, the second oil groove 21b, and the first oil port 12a in this order; meanwhile, a part of hydraulic oil at the outlet of the hydraulic motor sequentially passes through the third oil port 12c, the throttling channel 13 and the second oil port 12b and flows back to the inlet of the hydraulic motor;

when the fourth oil port 12d and the first oil port 12a are respectively connected with the pump body inlet and the pump body outlet, and the third oil port 12c and the second oil port 12b are respectively connected with the hydraulic motor inlet and the hydraulic motor outlet; the hydraulic oil in the third port 12c is returned through the second orifice 13b, the fifth oil groove 21e, and the fourth port 12d in this order; meanwhile, a part of the hydraulic oil at the outlet of the hydraulic motor sequentially flows back to the inlet of the hydraulic motor through the second oil port 12b, the throttling passage 13 and the third oil port 12c, thereby supplementing the flow rate at the inlet of the hydraulic motor.

It should be noted that the terms "first", "second", and the like are used to define the components, and are only used for convenience of distinguishing the corresponding components, and the terms have no special meanings unless otherwise stated, and therefore, the scope of the present invention should not be construed as being limited.

The features of the above embodiments may be arbitrarily combined, and for the sake of brevity, all possible combinations of the features in the above embodiments are not described, but should be construed as being within the scope of the present specification as long as there is no contradiction between the combinations of the features.

It should be understood by those skilled in the art that the above embodiments are only for illustrating the present invention and are not to be used as a limitation of the present invention, and that suitable changes and modifications of the above embodiments are within the scope of the claimed invention as long as they are within the spirit and scope of the present invention.

Claims

1. A threaded cartridge type balance valve comprises a valve sleeve and a valve core, wherein the valve sleeve is provided with a valve cavity, a first chamber and a second chamber, and the valve core is slidably installed in the valve cavity; the first chamber and the second chamber are respectively positioned at two ends of the valve sleeve;

the valve is characterized in that the outer wall of the valve sleeve is provided with a first oil port, a second oil port, a third oil port, a fourth oil port, a first throttle hole, a second throttle hole and a throttle channel, the first oil port is communicated with the first chamber, the second oil port is respectively communicated with the first throttle hole and the throttle channel, the third oil port is respectively communicated with the second throttle hole and the throttle channel, and the fourth oil port is communicated with the second chamber;

2. The threaded cartridge type balance valve according to claim 1, wherein the throttling channel comprises a third throttling hole and a fourth throttling hole, the valve core is provided with a first oil groove, the third throttling hole is communicated with the second oil port, and the fourth throttling hole is communicated with the third oil port;

when the valve core slides to the center position of the valve cavity, the first oil groove is communicated with the third throttling hole and the fourth throttling hole respectively.

3. The threaded cartridge type balance valve according to claim 2, wherein the valve core is further provided with a second oil groove, a third oil groove, a fourth oil groove and a fifth oil groove; the second oil groove is communicated with the first oil port, and the fifth oil groove is communicated with the fourth oil port;

the second oil groove is selectively communicated with the first throttling hole and/or the second oil port along with the movement of the valve core;

the third oil groove can be communicated with the second oil port;

the fourth oil groove can be communicated with the third oil port;

the fifth oil groove selectively communicates with the third oil port and/or the second orifice.

4. The threaded cartridge type balance valve according to claim 3, wherein a fifth orifice and a sixth orifice are further opened on the outer wall of the valve sleeve, and the fifth orifice is respectively communicated with the first chamber and the first oil port; the sixth throttle hole is communicated with the second chamber and the fourth oil port respectively;

5. The threaded cartridge type balance valve according to claim 4, wherein the spool comprises a first portion and a second portion, the first portion defines a first channel and the second portion defines a fourth channel along an axial direction of the spool;

a second channel and a third channel are formed in the first part along the radial direction of the valve core, the first channel is respectively communicated with the second channel and the third channel, the second channel is communicated with the second oil groove, and the third channel is communicated with the third oil groove;

fifth passageway and sixth passageway have been seted up to the second part, the fourth passageway respectively with the fifth passageway sixth passageway intercommunication, the fifth passageway with the fourth oil groove intercommunication, the sixth passageway with the fifth oil groove intercommunication.

6. The threaded cartridge balance valve of claim 5, further comprising a first seal member disposed within the first passageway and positioned between the second passageway and the first chamber and in sealing contact with an inner wall of the first passageway; the second seal is disposed in the second channel, and the second seal is located between the sixth channel and the second chamber and is in sealing contact with an inner wall of the second channel.

7. The threaded cartridge type balance valve according to claim 6, wherein when the pressure of the second chamber is higher than that of the first chamber, the spool moves to the left, hydraulic oil enters the hydraulic motor inlet through the fourth oil port, the fifth oil groove and the third oil port in sequence and flows into the second oil port through the hydraulic motor outlet, and hydraulic oil of the second oil port flows into the second oil groove through the third oil groove, the third passage, the first passage and the second passage and enters the first oil port to flow back to the oil tank;

8. The threaded cartridge type balance valve of claim 7, further comprising a valve seat, a third sealing member, a first resilient member, and a second resilient member, wherein the valve seat defines a notch, and wherein one end of the valve sleeve sealingly extends into and is mounted in the notch; the notch, the inner wall of the valve sleeve and one end of the valve core close to the valve seat form the first chamber, the first elastic piece is arranged in the first chamber, and two ends of the first elastic piece respectively abut against the valve seat and the valve core;

9. The threaded cartridge balance valve of claim 8, wherein the valve seat has a first step at an end thereof adjacent to the notch, and the valve sleeve has a protrusion thereon, the protrusion abutting against the first step when the end of the valve sleeve is inserted into and installed in the notch.

10. The threaded cartridge type balance valve according to claim 9, further comprising a first seal ring, a second seal ring and a third seal ring sleeved on the outer wall of the valve sleeve, wherein the fifth orifice and the first oil port are sequentially arranged between the protrusion and the first seal ring; the first throttling hole, the second oil port and the third throttling hole are sequentially distributed between the first sealing ring and the second sealing ring; the fourth throttling hole, the third oil port and the second throttling hole are sequentially distributed between the second sealing ring and the third sealing ring; and a fourth oil port and a sixth throttling hole are sequentially distributed between the third sealing ring and the third sealing element.