WO2021056306A1 - 预压阀和液压换向阀 - Google Patents

预压阀和液压换向阀 Download PDF

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Publication number
WO2021056306A1
WO2021056306A1 PCT/CN2019/108042 CN2019108042W WO2021056306A1 WO 2021056306 A1 WO2021056306 A1 WO 2021056306A1 CN 2019108042 W CN2019108042 W CN 2019108042W WO 2021056306 A1 WO2021056306 A1 WO 2021056306A1
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WO
WIPO (PCT)
Prior art keywords
valve
pressure
housing
inner cavity
valve seat
Prior art date
Application number
PCT/CN2019/108042
Other languages
English (en)
French (fr)
Inventor
王伟
Original Assignee
博世力士乐（北京）液压有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 博世力士乐（北京）液压有限公司 filed Critical 博世力士乐（北京）液压有限公司
Priority to PCT/CN2019/108042 priority Critical patent/WO2021056306A1/zh
Priority to DE112019007746.5T priority patent/DE112019007746T5/de
Priority to CN201980100783.1A priority patent/CN114450513B/zh
Publication of WO2021056306A1 publication Critical patent/WO2021056306A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure

Definitions

  • This application relates to the technical field of hydraulic control, and in particular to a pre-pressure valve and a hydraulic directional valve including such a pre-pressure valve.
  • various walking machinery such as loaders, excavators, cranes, etc. usually use the hydraulic cylinders of the boom and/or bucket to complete lifting, reversing, and falling actions.
  • the switching of these actions needs to be realized by a multi-channel hydraulic reversing valve.
  • the hydraulic cylinder retracts, that is, the oil on the piston side of the hydraulic cylinder flows out.
  • a pre-pressure valve also called a back pressure valve
  • a pre-pressure valve is usually set in the oil return line where the oil flows back to the oil tank to limit the oil Flow back to the oil tank, so that as much oil from the piston side as possible flows into the rod side.
  • the existing pre-pressure valve provides pre-pressure (also called back pressure) through a spring
  • the pre-pressure pressure is basically fixed throughout the working cycle (for example, the boom hydraulic cylinder is ejected and retracted) of.
  • the oil needs to be pumped into the piston side of the boom hydraulic cylinder through a pump, and accordingly the oil on the rod side will flow back to the oil tank.
  • the pump must provide additional pressure to overcome the pre-pressure pressure (for example, expressed in pressure, 10 bar) to return the oil to the tank.
  • the engine of the mobile machine needs to consume more energy.
  • the existing hydraulic directional valve adds an additional oil return channel to provide a channel without pre-pressure in the hydraulic system, so when the boom hydraulic cylinder is ejected, the oil never has pre-pressure The channel flows back to the fuel tank.
  • this solution makes the valve body casting of the hydraulic directional valve larger, the valve stem is more complicated, and the cost is higher.
  • the purpose of this application is to provide an improved pre-pressure valve to solve the problem that the pre-pressure pressure in the prior art is basically unchanged during the entire working cycle, and the hydraulic directional valve including such a pre-pressure valve is too large and costly. And energy waste.
  • a pre-pressure valve including: a housing having a housing inner cavity, the housing inner cavity having a first opening and a second opening; a valve seat, so The valve seat is configured to be movably received in the first opening of the inner cavity of the housing, and the first end of the valve seat bears hydraulic pressure; wherein, the pre-pressure valve further includes a pin shaft, the pin The shaft is configured to be movably received in the inner cavity of the housing, wherein the first end of the pin shaft and the second end of the valve seat are configured to be in contact with each other, fixedly coupled or integrated, and the pin The second end of the shaft receives hydraulic pressure from the second opening of the inner cavity of the housing.
  • a hydraulic directional valve comprising: a valve body provided with a pilot oil pipe; and the above-mentioned pre-pressure valve, wherein the first pressure valve in the housing cavity of the pre-pressure valve The two openings are connected with the pilot oil pipe.
  • the pre-pressure can be provided during the retraction phase of the hydraulic cylinder, but not during the ejection phase of the hydraulic cylinder . Therefore, the pre-pressure can be adjusted according to the action of the hydraulic cylinder, thereby saving fuel for the engine.
  • the hydraulic directional valve including the above-mentioned pre-pressure valve only needs one oil return passage, so that the structure of the valve body and the valve stem is simpler and more compact, and the cost can be further reduced.
  • Figure 1 is a schematic exploded perspective view of the pre-pressure valve of the present application
  • Figure 2 is a schematic cross-sectional view of the pre-pressure valve shown in Figure 1;
  • Fig. 3 is a schematic partial cross-sectional view of a hydraulic directional valve including the pre-pressure valve shown in Fig. 1.
  • the pre-pressure valve 100 of the present application roughly includes a housing 10, a valve seat 20, a valve core 30, a spring seat 40 and a spring 50. Different from the existing pre-pressure valve, the pre-pressure valve 100 of the present application further includes a pin 60.
  • the housing 10 has a housing inner cavity 11, and the housing inner cavity 11 has a first opening 12 and a second opening 13.
  • the pre-pressure valve 100 of the present application does not have too many restrictions, as long as it is convenient to install on the valve body 201 (shown in FIG. 3) of the hydraulic directional valve 200, and it can even be used.
  • the external shape of the housing with the pre-pressure valve may be provided with an external thread portion and an external hexagonal portion, so that the pre-pressure valve 100 can be directly screwed on the valve body 201 of the hydraulic directional valve 200 like a screw.
  • a groove 14 is also provided on the outside of the housing 10 of the pre-pressure valve 100 to receive the sealing ring 16. It should be understood that the shape and structure of the outer side of the housing 10 of the pre-pressure valve 100 and the cooperation with other components are not intended to limit the application.
  • the valve seat 20 is configured to be movably received in the first opening 12 of the housing inner cavity 11, and the valve seat 20 is provided with an oil inlet 22 and an oil outlet 21.
  • the oil outlet 21 is provided as a tapered opening formed at the first end 23 of the valve seat 20, and the oil inlet 22 is provided as a through hole that communicates with the oil outlet 21 laterally.
  • the oil outlet 21 can be communicated with the oil return line 202 of the hydraulic directional valve 200, and the oil inlet 22 can be communicated with an oil tank (not shown) through a line 203 (shown in FIG. 3), so as to pass through when needed.
  • the path between the valve seat 20 and the valve core 30 replenishes the hydraulic circuit with oil.
  • the outer shape of the second end 24 of the valve seat 20 is consistent with the inner shape of the first opening 12 of the housing inner cavity 11, so that the valve seat 20 can be guided to move in the first opening 12 of the housing inner cavity 11.
  • the valve core 30 is configured to be able to form a seal with the oil outlet 21 of the valve seat 20.
  • the first end 31 of the valve core 30 is a cone
  • the second end 32 is a cylinder
  • the tapered surface of the first end 31 can form a seal with the oil outlet 21 of the valve seat 20.
  • the oil outlet 21 of the valve seat 20 can be configured as a tapered opening.
  • the valve core 30 is movably received in the valve seat 20.
  • the pre-pressure valve 100 of the present application is not limited to the shape and arrangement structure of the valve seat 20 and the valve core 30 as shown in the figure.
  • a valve core with a spherical surface and a valve seat with a tapered surface can be used in In the pre-pressure valve of this application.
  • the spring seat 40 and the spring 50 are assembled between the valve core 30 and the valve seat 20, and the spring 50 exerts an elastic force that seals the valve core 30 and the oil outlet 21 of the valve seat 20.
  • the spring seat 40 can be held on the second end 32 of the valve core 30 by the locking ring 41, and the spring 50 is installed around the valve core 30 and is restricted by the spring seat 40.
  • the pre-compression valve 100 of the present application no longer includes a spring for applying a fixed pre-compression pressure, but uses a pin 60 to provide the pre-compression pressure.
  • the pin 60 is configured to be movably received in the housing cavity 11 of the housing 10, wherein the first end 61 of the pin 60 and the second end 24 of the valve seat 20 are in contact with each other, and the second end 62 of the pin 60 is in contact with each other.
  • the hydraulic pressure from the second opening 13 of the inner cavity 11 of the housing is received.
  • the second opening 13 of the inner cavity 11 of the housing may be provided with an internal thread 15 for connecting with the pilot oil pipe (not shown) of the hydraulic directional valve 200. How the pre-pressure valve 100 cooperates with the hydraulic directional valve 200 to provide the pre-pressure pressure through the pilot pressure will be described in further detail below with reference to FIG. 3.
  • the second end 62 of the pin 60 can form a liquid seal with the inner cavity 11 of the housing to ensure the transmission of the pilot pressure.
  • the first end 61 of the pin shaft 60 may be provided with a first cavity 63, and the spring seat 40, the spring 50 and the valve core 30 may be received in the first cavity 63 to guide the spring seat 40, the spring 50 and the valve core 30 sports.
  • the second end 24 of the valve seat 20, that is, the end opposite to the oil outlet 21, can be provided with a second cavity 25, and the second cavity 25 can receive the first end 61 of the pin 60. In this way, the valve seat 20, the pin shaft 60, and the valve core 30 form a nested assembly, so that the components maintain a concentric configuration.
  • At least one step may be provided in the inner cavity 11 of the housing, as shown in FIG. 2.
  • a certain gap can be maintained between the wall of the inner cavity 11 of the housing and the first end 61 of the pin shaft 60 so as not to affect the movement of the pin shaft 60.
  • the wall of the first cavity 63 of the pin shaft 60 may be provided with a through hole 64 to allow the first cavity 63 to communicate with the inner cavity 11 of the housing to achieve internal and external pressure balance.
  • the pre-pressure valve 100 of the present application may only include a housing without replenishing oil from the oil inlet 22 and the oil outlet 21 of the valve seat 20. 10.
  • the first end 23 of the valve seat 20 may have an end surface that bears hydraulic pressure, and the second end 24 of the valve seat 20 and the first end 61 of the pin 60 may be in contact with each other, fixedly connected or integrated.
  • the pre-pressure valve 100 of the present application omits the valve core 30, the spring 50 and the spring seat 40, and the structure is simpler.
  • the hydraulic directional valve 200 including the above-mentioned pre-pressure valve 100 of the present application and its working process will be described below with reference to FIG. 3.
  • the hydraulic directional valve 200 of the present application includes a valve body 201, and the valve body 201 may be provided with a pilot oil pipe (not shown).
  • the pre-pressure valve 100 can be installed in the valve body 201 of the hydraulic directional valve 200 such that the end surface of the first end 23 of the valve seat 20 abuts against the port of the oil return line 202 of the valve body 201 to seal the oil return line 202.
  • the pre-pressure valve 100 can be connected and fixed with the valve body 201 through threads.
  • the second opening 13 of the housing inner cavity 11 of the pre-pressure valve 100 can be connected with a pilot oil pipe.
  • the operator pulls the joystick to cause the pilot pressure in the pilot oil pipe to act on the second end of the pin shaft 60, and is transmitted to the valve seat 20 and the valve core 30 through the pin shaft 60, so that The first end 23 of the valve seat 20 abuts on the valve body 201 of the hydraulic directional valve 200 to provide pre-pressure pressure for the oil to be returned to the oil tank. Therefore, under the limitation of the preload pressure, the oil flowing from the piston side of the boom hydraulic cylinder will flow into the rod side of the boom hydraulic cylinder as much as possible, so as to achieve more effective oil recovery.
  • the ratio of the effective area of the second end 62 of the pin 60 to the effective area of the valve seat 20 is set according to the pre-pressure of the pre-pressure valve 100, where the effective area refers to the hydraulic The effective area of pressure.
  • the relationship between the pre-pressure of the pre-pressure valve 100 and the pilot pressure of the joystick is explained below by way of example.
  • the pilot pressure generated by the operating rod of the hydraulic directional valve 200 can be set to P1 (indicated by pressure), which acts on the second end 62 of the pin 60, and the effective area of the second end 62 of the pin 60 is set For S1.
  • the pre-pressure valve of the present application can use the pilot pressure from the operating lever of the hydraulic directional valve to provide the pre-pressure by setting the pin shaft, so that the pre-pressure can be provided when the pre-pressure is required, and the pre-pressure is not required. No pre-pressure is provided during pressure.
  • This adjustable pre-pressure valve reduces the energy consumption of the engine, and does not need to provide an additional oil return channel on the valve body of the hydraulic directional valve, so that the valve body of the hydraulic directional valve is smaller in size and lower in cost.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

公开了一种预压阀（100），包括：壳体（10），具有壳体内腔（11），壳体内腔具有第一开口（12）和第二开口（13）；阀座（20），被配置成可移动地接收在壳体内腔的第一开口中，且阀座的第一端（23）承受液压压力；预压阀还包括销轴（60），销轴被配置成可移动地容纳在壳体内腔中，销轴的第一端（61）与阀座的第二端（24）被配置成相互接触、固定连接或成为一体，且销轴的第二端（62）接收来自壳体内腔的第二开口的液压压力。还公开了一种包括预压阀的液压换向阀（200）。该预压阀可降低功率损失，使液压换向阀的阀体尺寸更小，成本更低。

Description

预压阀和液压换向阀 技术领域
本申请涉及液压控制技术领域，尤其涉及一种预压阀及包括这种预压阀的液压换向阀。
背景技术
比如装载机、挖掘机、起重机等各种行走机械，通常要利用动臂和/或铲斗的液压缸等来完成举升、反转、下落等动作。这些动作的切换需要通过多路液压换向阀来实现。例如，当需要完成下落动作时，液压缸回缩，即液压缸的活塞一侧的油液流出。为实现油液回收并使油液尽可能多地流入液压缸的杆一侧，通常在油液流回油箱的回油管路中设置预压阀(也称为背压阀)，以限制油液流回油箱，从而使得从活塞一侧流出的油液尽可能多地流入杆一侧。
由于现有的预压阀是通过弹簧来提供预压压力(也称为背压)的，所以在整个工作循环(例如，动臂液压缸顶出和回缩)中预压压力都是基本固定的。当动臂液压缸顶出时，需要通过泵将油液泵入动臂液压缸的活塞一侧，相应地杆一侧的油液将流回油箱。但是，由于在油液流回油箱的回油管路中设有预压阀，所以泵必须提供额外的压力来克服预压压力(例如，以压强来表示，10巴)才能使油液返回油箱。相应地，行走机械的发动机需要消耗更多的能源。
为解决这一问题，现有的液压换向阀增加了额外的回油通道，以在液压系统中提供无预压压力的通道，所以当动臂液压缸顶出时油液从没有预压压力的通道流回油箱。然而，这种解决方案使液压换向阀的阀体铸件尺寸更大、阀杆更复杂且成本更高。
因此，有必要改进现有的预压阀和液压换向阀，以克服现有技术中存 在的问题。
发明内容
本申请的目的在于提供一种改进的预压阀，以解决现有技术中在整个工作循环期间预压压力基本不变、包括这种预压阀的液压换向阀体积过大、成本过高和能源浪费的问题。
为此，根据本申请的一方面，提供了一种预压阀，包括：壳体，所述壳体具有壳体内腔，所述壳体内腔具有第一开口和第二开口；阀座，所述阀座被配置成可移动地接收在所述壳体内腔的第一开口中，且所述阀座的第一端承受液压压力；其中，所述预压阀还包括销轴，所述销轴被配置成可移动地容纳在所述壳体内腔中，其中所述销轴的第一端与所述阀座的第二端被配置成相互接触、固定联接或成为一体，且所述销轴的第二端接收来自所述壳体内腔的第二开口的液压压力。
根据本申请的另一方面，提供了一种液压换向阀，包括：阀体，所述阀体设有先导油管；和上述的预压阀，其中所述预压阀的壳体内腔的第二开口与所述先导油管连接。
根据本申请，通过将现有预压阀中的固定弹簧替换为与先导油管液压联接的销轴，可以在液压缸回缩阶段提供预压压力，而在液压缸顶出阶段不提供预压压力。因此，可以根据液压缸的动作而调整预压压力，从而节省发动机的燃料。并且，包括上述预压阀的液压换向阀只需要一个回油通道，使阀体和阀杆的结构更简单、更紧凑，从而可以进一步降低成本。
附图说明
下面将参照附图对本申请的示例性实施例进行详细描述。需要指出的是，各附图的比例出于清楚说明的目的可能不同，但这并不影响对本申请的理解。在附图中：
图1是本申请的预压阀的示意性分解透视图；
图2是图1所示的预压阀的示意性剖视图；
图3是包括图1所示的预压阀的液压换向阀的示意性局部剖视图。
具体实施方式
下面结合示例详细描述本申请的示例性实施例。但是，本领域技术人员应当理解，这些示例性实施例并不意味着对本申请形成任何限制。此外，在不冲突的情况下，本申请的实施例中的特征可以相互组合。在不同的附图中，相同或相似的部件用相同的附图标记表示，且为简要起见，省略了其它的部件，但这并不表明本申请的预压阀和液压换向阀不可包括其它部件或部分。应当理解，附图中各部件的尺寸、比例关系以及部件的数目均不作为对本申请的限制。
下面参照图1和2来描述本申请的预压阀。在如图1所示的实施例中，本申请的预压阀100大致包括壳体10、阀座20、阀芯30、弹簧座40和弹簧50。与现有预压阀不同的是，本申请的预压阀100还包括销轴60。
壳体10具有壳体内腔11，壳体内腔11具有第一开口12和第二开口13。对于壳体10的外部形状，本申请的预压阀100并没有过多的限制，只要便于装在液压换向阀200的阀体201(图3中示出)上即可，甚至可以采用现有预压阀的壳体的外部形状。例如，壳体10的外侧可以设有外螺纹部分和外六角部分，这样可以像拧螺钉一样将预压阀100直接拧紧在液压换向阀200的阀体201上。另外，考虑到与液压换向阀200之间的密封，预压阀100的壳体10外侧还设有凹槽14，以接收密封圈16。应理解的是，预压阀100的壳体10外侧的形状、结构及与其它部件的配合并不作为对本申请的限制。
阀座20被配置成可移动地接收在壳体内腔11的第一开口12中，且阀座20设有进油口22和出油口21。在所示的实施例中，出油口21被设 置成在阀座20的第一端23形成的锥形开口，而进油口22被设置成与出油口21横向地连通的通孔。当将预压阀100组装在液压换向阀200的阀体201上时，阀座20的第一端23的端面密封液压换向阀200的回油管路202的端口(图3中示出)，承受来自返回的油液的液压压力。出油口21可以与液压换向阀200的回油管路202连通，而进油口22则可以通过管路203(图3中示出)与油箱(未示出)连通，从而在需要时经阀座20和阀芯30之间的路径给液压回路补充油液。阀座20的第二端24的外部形状与壳体内腔11的第一开口12的内部形状一致，使得阀座20可以在壳体内腔11的第一开口12内被引导移动。
阀芯30被配置成能够与阀座20的出油口21形成密封。例如，阀芯30的第一端31为锥体，第二端32为圆柱体，第一端31的锥形表面可与阀座20的出油口21形成密封。相应地，阀座20的出油口21可以设置成锥形开口。阀芯30可移动地容纳在阀座20中。这样，当阀芯30的第一端31和阀座20的第一端23的端面承受来自返回油液的液压压力时，阀芯30和阀座20移动，以解除与液压换向阀200的阀体201之间的密封，使油液返回油箱。应指出的是，本申请的预压阀100并不限于如图所示的阀座20和阀芯30的形状和布置结构，例如，具有球面的阀芯和具有锥面的阀座都可用在本申请的预压阀中。
在组装状态下，弹簧座40和弹簧50被装配在阀芯30和阀座20之间，并使弹簧50施加使阀芯30与阀座20的出油口21形成密封的弹力。弹簧座40可通过锁定环41保持在阀芯30的第二端32上，且弹簧50围绕阀芯30安装并通过弹簧座40限位。
本申请的预压阀100不再包括施加固定的预压压力的弹簧，而是采用销轴60来提供预压压力。销轴60被配置成可移动地容纳在壳体10的壳体内腔11中，其中销轴60的第一端61与阀座20的第二端24相互接触，销轴60的第二端62接收来自壳体内腔11的第二开口13的液压压力。相 应地，壳体内腔11的第二开口13可设有内螺纹15，以用于与液压换向阀200的先导油管(未示出)连接。将在下面参照图3进一步详细描述预压阀100如何与液压换向阀200配合以通过先导压力来提供预压压力。
另外，销轴60的第二端62可与壳体内腔11形成液体密封，以确保先导压力的传递。销轴60的第一端61可设有第一凹腔63，且弹簧座40、弹簧50和阀芯30可被接收在第一凹腔63中，以引导弹簧座40、弹簧50和阀芯30的运动。阀座20的第二端24，即与出油口21相反的一端，可设有第二凹腔25，第二凹腔25可接收销轴60的第一端61。这样，阀座20、销轴60和阀芯30形成嵌套的组件，以使各部件保持同心的配置。
为限制阀座20和销轴60在壳体内腔11中的移动距离，壳体内腔11中可以设有至少一个台阶，如图2所示。壳体内腔11的壁与销轴60的第一端61之间可保持一定的间隙，以免影响销轴60的移动。另外，销轴60的第一凹腔63的壁可设有通孔64，以使第一凹腔63与壳体内腔11连通，实现内外压力平衡。
以上结合图1和2描述了本申请的预压阀100的结构。应指出的是，根据本申请的另一实施例，在不需要从阀座20的进油口22和出油口21补充油液的情况下，本申请的预压阀100可以只包括壳体10、阀座20和销轴60，其中阀座20可以不再包括进油口22和出油口21。这样，阀座20的第一端23可以具有承受液压压力的端面，且阀座20的第二端24可以和销轴60的第一端61相互接触、固定连接或成为一体。在不需要补充油液的情况下，本申请的预压阀100省略了阀芯30、弹簧50和弹簧座40，结构更简单。
下面参照图3描述本申请的包括上述预压阀100的液压换向阀200及其工作过程。
如图3所示，本申请的液压换向阀200包括阀体201，阀体201可设有先导油管(未示出)。预压阀100可安装在液压换向阀200的阀体201 中，使得阀座20的第一端23的端面抵靠阀体201的回油管路202的端口，以密封回油管路202。预压阀100可通过螺纹与阀体201连接固定。预压阀100的壳体内腔11的第二开口13可与先导油管连接。当需要例如动臂液压缸回缩时，操作人员扳动操纵杆，使先导油管内的先导压力作用在销轴60的第二端，并经销轴60传递到阀座20以及阀芯30，使得阀座20的第一端23抵靠在液压换向阀200的阀体201上，给待返回油箱的油液提供预压压力。所以，在预压压力的限制下，从动臂液压缸的活塞一侧流出的油液将尽可能多地流入动臂液压缸的杆一侧，从而实现更有效的油液回收。当需要动臂液压缸顶出时，操作人员扳动操纵杆实现液压换向，而使先导油管不再存在先导压力，所以预压阀100不再提供预压压力。待返回油箱的油液将推动阀座20、阀芯30和销轴60如图3所示向左移动，这样，在动臂液压缸顶出时就不需要泵提供额外的10巴压力，从而可以节省发动机的能源消耗。
为保证提供预定的预压压力，销轴60的第二端62的作用面积与阀座20的作用面积的比值是根据预压阀100的预压压力设定的，其中作用面积是指承受液压压力的有效面积。下面通过示例的方式解释预压阀100的预压压力与操纵杆的先导压力的关系。例如，液压换向阀200的操纵杆产生的先导压力可以设为P1(以压强来表示)，该压力作用在销轴60的第二端62，销轴60的第二端62的作用面积设为S1。在阀座20与液压换向阀200的阀体201接触的位置，形成密封的阀座20的作用面积设为S2，所产生的压力(即，预压压力)设为P2(同样以压强来表示)，则根据计算公式可知，P1*S1＝P2*S2，所以，P2＝(P1*S1)/S2。当先导压力P1＝35巴，销轴60的第二端62的直径为13.58mm(即，S1＝144.70mm 2)时，只要将阀座20的第一端23的端面中承受液压压力的部分的直径(等于液压换向阀200的回油管路202的端口直径)设为25.40mm(即，S2＝506.45mm 2)，则可以根据上述公式计算出预压压力P2＝10巴。
根据本申请的实施例，对于5至9吨的轮式装载机的液压系统来说，可以节约大约3.9％的能量，具体实验数据如表1中所示。
Figure PCTCN2019108042-appb-000001
从表1可以看出，当动臂液压缸顶出时，如果需要在回油管路中克服10.8巴的预压压力，则需要消耗8.64Kw的功率，而动臂液压缸正常工作时的工作压力为280巴，需要消耗224Kw的功率。因此，通过采用本申请的预压阀，在动臂液压缸顶出时没有预压压力，所以可以节省8.64/224＝3.9％的能量。对于铲斗液压缸来说，基于上述原理，可以实现同样的能量节省，因此，本文不再对此进一步详细描述。
所以，本申请的预压阀通过设置销轴可以利用来自液压换向阀的操纵杆的先导压力来提供预压压力，从而可以在需要预压压力时提供预压压力，而在不需要预压压力时不提供预压压力。这种可调整的预压阀降低了发动机的能源消耗，且不需要在液压换向阀的阀体上设置额外的回油通道，使液压换向阀的阀体尺寸更小，成本更低。
以上结合具体实施例对本申请进行了详细描述。显然，以上描述以及在附图中示出的实施例均应被理解为是示例性的，而不构成对本申请的限制。对于本领域技术人员而言，可以在不脱离本申请的精神的情况下对其进行各种变型或修改，这些变型或修改均不脱离本申请的范围。

Claims (11)

  1. 一种预压阀，包括：
    壳体(10)，所述壳体(10)具有壳体内腔(11)，所述壳体内腔(11)具有第一开口(12)和第二开口(13)；
    阀座(20)，所述阀座(20)被配置成可移动地接收在所述壳体内腔(11)的第一开口(12)中，且所述阀座(20)的第一端(23)承受液压压力；
    其特征在于，所述预压阀(100)还包括销轴(60)，所述销轴(60)被配置成可移动地容纳在所述壳体内腔(11)中，其中所述销轴(60)的第一端(61)与所述阀座(20)的第二端(24)被配置成相互接触、固定连接或成为一体，且所述销轴(60)的第二端(62)接收来自所述壳体内腔(11)的第二开口(13)的液压压力。
  2. 根据权利要求1所述的预压阀，其特征在于，所述销轴(60)的第二端(62)的作用面积与所述阀座(20)的第一端(23)的作用面积的比值是根据所述预压阀(100)的预压压力设定的。
  3. 根据权利要求1或2所述的预压阀，其特征在于，在所述销轴(60)的第一端(61)与所述阀座(20)的第二端(24)被配置成相互接触的构造中，所述阀座(20)还设有进油口(22)和出油口(21)，且所述预压阀还包括；
    阀芯(30)，所述阀芯(30)被配置成能够与所述阀座(20)的出油口(21)形成密封；和
    弹簧座(40)和弹簧(50)，所述弹簧座(40)和所述弹簧(50)被装配在所述阀芯(30)和所述阀座(20)之间，使得所述弹簧(50)施加 使所述阀芯(30)与所述阀座(20)的出油口(21)形成密封的弹力。
  4. 根据权利要求3所述的预压阀，其特征在于，所述销轴(60)的第一端(61)设有第一凹腔(63)，且所述弹簧座(40)、所述弹簧(50)和所述阀芯(30)被接收在所述第一凹腔(63)中。
  5. 根据权利要求4所述的预压阀，其特征在于，所述阀座(20)的第二端(24)设有第二凹腔(25)，所述第二凹腔(25)接收所述销轴(60)的第一端(61)。
  6. 根据权利要求1至5中的任一项所述的预压阀，其特征在于，在所述壳体内腔(11)中设有至少一个台阶，以限制所述阀座(20)和/或所述销轴(60)的移动距离。
  7. 根据权利要求1至6中的任一项所述的预压阀，其特征在于，所述壳体内腔(11)的第二开口(13)设有内螺纹(15)，以用于与液压换向阀的先导油管连接。
  8. 根据权利要求1至7中的任一项所述的预压阀，其特征在于，所述销轴(60)的第二端(62)与所述壳体内腔(11)的壁形成液体密封。
  9. 根据权利要求4所述的预压阀，其特征在于，所述销轴(60)的第二端(62)与所述壳体内腔(11)的壁保持一定间隙，且所述销轴(60)的第一凹腔(63)的壁设有与所述壳体内腔(11)连通的通孔(64)。
  10. 一种液压换向阀，包括：
    阀体(201)，所述阀体(201)设有先导油管；和
    根据权利要求1至9中的任一项所述的预压阀，其中所述预压阀(100)的壳体内腔(11)的第二开口(13)与所述先导油管连接。
  11. 根据权利要求10所述的液压换向阀，其特征在于，所述预压阀(100)通过螺纹与所述阀体(201)连接，使得所述预压阀(100)的阀座(20)的第一端(23)的端面密封所述阀体(201)的回油管路(202)的端口。
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