CN116104725A - Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device - Google Patents

Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device Download PDF

Info

Publication number
CN116104725A
CN116104725A CN202310080991.8A CN202310080991A CN116104725A CN 116104725 A CN116104725 A CN 116104725A CN 202310080991 A CN202310080991 A CN 202310080991A CN 116104725 A CN116104725 A CN 116104725A
Authority
CN
China
Prior art keywords
pilot
fluid
piston
valve
valve core
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202310080991.8A
Other languages
Chinese (zh)
Inventor
张兴军
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to CN202310080991.8A priority Critical patent/CN116104725A/en
Publication of CN116104725A publication Critical patent/CN116104725A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/123Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
    • F04B9/127Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting elastic-fluid motor, e.g. actuated in the other direction by gravity or a spring
    • F04B9/1276Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting elastic-fluid motor, e.g. actuated in the other direction by gravity or a spring with fluid-actuated inlet or outlet valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10Valves; Arrangement of valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162Adaptations of cylinders
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22Arrangements for enabling ready assembly or disassembly

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

The invention relates to a fluid flow direction switching valve and an automatic control switching straight-path reciprocating power device, wherein the fluid flow direction switching valve is a two-position five-way reversing valve, pilot mechanisms are arranged on two sides of the fluid flow direction switching valve, a pilot fluid inlet and a pressure discharge port are arranged in the pilot mechanisms, and a one-way valve is arranged at the pilot fluid inlet; the power device comprises the fluid flow direction switching valve and a straight-travel reciprocating power cylinder body, and small holes are formed in the cylinder barrel and are used for being communicated with a pilot mechanism of the fluid flow direction switching valve to obtain a pilot signal. The automatic control switching straight-stroke reciprocating power device provided by the invention has no coil, does not need electric control, and has no reversing mechanism of mechanical collision.

Description

Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device
Technical Field
The invention relates to a multi-way valve and a piston machine for driving a workpiece, in particular to a fluid flow direction switching valve and an automatic control switching straight stroke reciprocating power device.
Background
In the prior art, a cylinder such as a pneumatic plunger pump belongs to a straight-travel automatic reciprocating cylinder. The piston is provided with a built-in reversing valve which is designed at the top of the piston. During reversing, the piston assembly will strike the compression spring on the cylinder front head and the truncated cone coil spring on the cylinder rear head. The spring has certain fatigue limit, and high-frequency mechanical collision is not only loud, but also greatly reduces the service life of the product. In addition, the booster pump for fluid pressurization is also a straight-path reciprocating cylinder, and the power part is provided with a built-in mechanical reversing valve which is not designed on the piston but on the front cover and the rear cover of the cylinder. When the cylinder moves linearly, the piston collides with the valve needle of the built-in reversing valve, and a reversing signal is obtained. However, the piston will remain moving for a distance in the original direction of movement because of the inertia of the piston and the insufficient air supply available after reversing to allow the piston to reverse immediately. Although this distance is very small, the piston can directly strike the front or rear cylinder head, causing a purely mechanical impact, and also quite noisy. This is also a design defect or a defect of the product.
The prior art power pumps for media (fluid) delivery employing straight travel reciprocating power units are limited to delivery functions. Because of the inability to start at low pressure (e.g., at 0.15-0.3MPa because the prior art reversing valve cannot achieve moving reversing at pressures of 0.3MPa or less), there are cases where the reversing valve cannot start after low pressure for a second time, and the reversing valve can start after assembly by disassembly (the secondary assembly manually positions the reversing valve at the limit after reversing). So that only high-pressure start-up is possible (use of 0.5-0.8MPa is required). As the supercharging function, the output pressure adjustable range is small, a wider output pressure range cannot be obtained, and the selection of the use pressure is relatively small, so that the supercharging device is not suitable for supercharging and pressure maintaining. In the straight-stroke automatic reciprocating plunger pump, a piston assembly can strike a compression spring on a front cover of a cylinder and a truncated cone spiral spring on a rear cover of the cylinder in operation, the spring has a certain fatigue limit, and high-frequency mechanical collision is realized, so that the noise is high, and the service life of a product is greatly reduced.
The pneumatic control valve in the prior art has five-port two-position double-acting pneumatic control valve types: 4a120, 4a220, 4a320, 4a420; EAV220, EAV320, EAV420, EAV620. The existing pneumatic control valves in the market can acquire signals from the port A and the port B, cannot be controlled by an independent unit, and can only work after being controlled by other valves. Because the compressed air obtained from the port A and the port B cannot be discharged by itself, the compressed air can be discharged only by controlling the electromagnetic valve, the manual valve, the hand-operated valve, the hand-rotating valve, the mechanical valve and the foot valve. The reversing valve core of the pneumatic control valve cannot be reversed without exhausting.
Disclosure of Invention
The invention aims to provide a fluid flow direction switching valve and an automatic control switching straight stroke reciprocating power device.
In order to solve the problems, the invention adopts the following technical scheme:
the fluid flow direction switching valve is a two-position five-way reversing valve and comprises a valve body, a valve cavity formed in the valve body, a reversing valve core arranged in the valve cavity in a sliding manner and a guide mechanism respectively arranged at the left side and the right side of the valve body, wherein five valve ports are arranged on the valve body, and the five valve ports are a pressure input port P, two fluid output ports and two fluid return ports;
the pilot mechanism comprises a pilot chamber shell, a pilot chamber formed in the pilot chamber shell and a pilot piston arranged in the pilot chamber, wherein the pilot piston is used for pushing the reversing valve core to move and reverse, and divides the pilot chamber into an inner chamber at one side of the reversing valve core and an outer chamber at the other side of the reversing valve core;
the pilot chamber shell is provided with a pilot fluid inlet and a fluid pressure discharge hole which are communicated with the outer chamber, and a one-way valve is arranged on the internal or external air path of the pilot fluid inlet.
As a further improvement of the invention, at least one outer chamber of the pilot mechanism is communicated with the pressure input port through a regulating channel, and the pilot mechanism is provided with a control mechanism for controlling the on-off of the regulating channel.
As a further improvement of the present invention, the control mechanism includes a control button provided on a pilot chamber housing of the pilot mechanism and a pilot spool provided in the pilot chamber housing of the pilot mechanism, the pilot spool closing the adjustment passage in a stationary state, and depressing the control button to move the pilot spool to open the adjustment passage.
As a further improvement of the invention, a fluid nozzle and a pilot valve core seat are fixedly arranged in a pilot chamber shell of a pilot mechanism provided with the control mechanism, a fluid outlet is arranged on the fluid nozzle, the tail end of the regulating channel is communicated with the fluid outlet, the pilot valve core is slidably arranged on the pilot valve core seat, a valve core reset spring is arranged between the pilot valve core and the pilot valve core seat, and the valve core reset spring enables the pilot valve core to seal the fluid outlet in a static state.
As a further improvement of the present invention, the pilot chamber housing of the pilot mechanism provided with the control mechanism includes a pilot chamber main housing and a pilot chamber end cover, the pilot chamber is provided in the pilot chamber main housing, the pilot fluid inlet is provided on the pilot chamber end cover, spool mounting holes are provided in the pilot chamber main housing and the pilot chamber end cover, the pilot spool and the pilot spool seat are provided in the spool mounting holes, the control button is provided on the pilot chamber main housing, and the fluid nozzle is provided in the pilot chamber main housing.
As a further improvement of the invention, a first pore canal communicated with the fluid outlet is arranged in the pilot chamber main shell, a second pore canal communicated with the pressure input port is arranged in the valve body, the first pore canal is communicated with the pore canal, and the first pore canal and the second pore canal form the regulating channel.
As a further improvement of the invention, the check valve is arranged in the internal gas path of the pilot fluid inlet, a check valve mounting hole is arranged in the pilot chamber shell, the check valve comprises a check valve rod arranged in the check valve mounting hole, a sealing ring is arranged on the top of the check valve rod, the check valve plug and the sealing ring are used for sealing the pilot fluid inlet from the inside, a spring is sleeved on the check valve rod, a cylindrical adjusting screw is arranged in the check valve mounting hole, the spring is arranged between the adjusting screw and the check valve rod, the adjusting screw is in threaded fit with the check valve mounting hole, and the outermost end of the check valve mounting hole is provided with a mounting hole plug.
The invention also provides an automatic control switching straight-stroke reciprocating power device, which comprises the fluid flow direction switching valve and the straight-stroke reciprocating power cylinder body, wherein the straight-stroke reciprocating power cylinder body comprises a cylinder barrel, a front end cover and a rear end cover which are arranged at two ends of the cylinder barrel in a sealing manner, and a piston arranged in the cylinder barrel, a piston cavity for accommodating the piston is formed in the cylinder barrel, the piston divides the piston cavity into a front piston cavity and a rear piston cavity, and a first pilot fluid output hole and a second pilot fluid output hole are arranged on the wall of the cylinder barrel.
As a further improvement, the first pilot fluid output hole and the second pilot fluid output hole are respectively arranged at two sides of a central line in the length direction of the cylinder barrel; preferably, the first pilot fluid output hole and the second pilot fluid output hole are symmetrically arranged with respect to a center line of the cylinder in the longitudinal direction.
The number of the first pilot fluid output holes and the second pilot fluid output holes is N, and N is a positive integer greater than or equal to 1; the first pilot fluid output hole and the second pilot fluid output hole can be round holes or threaded holes, also can be kidney-shaped holes, and are respectively distributed and arranged along the circumferential direction of the cylinder barrel;
When the piston moves to the front end of the cylinder barrel, the piston seals the second pilot fluid output hole, and the first pilot fluid output hole is communicated with the rear piston cavity;
when the piston moves to the rear end of the cylinder barrel, the piston seals the first pilot fluid output hole, and the second pilot fluid output hole is communicated with the front piston cavity;
the front end cover is provided with a front fluid inlet and a front fluid outlet which are communicated with the front piston cavity, and the rear end cover is provided with a rear fluid inlet and a rear fluid outlet which are communicated with the rear piston cavity;
the front fluid inlet and the rear fluid inlet are respectively communicated with two fluid output ports on the fluid flow direction switching valve, and the first pilot fluid output hole and the second pilot fluid output hole are respectively communicated with a pilot fluid inlet of a pilot mechanism on the corresponding side of the fluid flow direction switching valve.
Further, a piston rod is fixedly arranged on the piston, the piston rod penetrates through the front end cover and extends out of the piston cavity, and a sealing mechanism is arranged between the piston rod and the front end cover.
Further, when the piston moves to the front end of the cylinder barrel to enable the first pilot fluid output hole to be communicated with the rear piston cavity, a buffer gap exists between the front end of the piston and the front end cover;
When the piston moves to the rear end of the cylinder barrel to enable the second pilot fluid output hole to be communicated with the front piston cavity, a buffer gap exists between the rear end of the piston and the rear end cover.
The beneficial effects of adopting above-mentioned technical scheme to produce lie in:
in the fluid flow direction switching valve provided by the invention, the pilot fluid inlet and the fluid pressure discharge hole are arranged on the pilot mechanism at two sides of the fluid flow direction switching valve, and the one-way valve is arranged on the internal or external air path of the pilot fluid inlet, so that the pilot fluid inlet can only allow fluid to enter and not discharge, and the fluid pressure discharge hole is used for discharging the fluid in the pilot cavity to play a role of pressure relief.
Under the condition that the pilot mechanism is provided with the control mechanism, because the outer chamber of the pilot mechanism is communicated with the pressure input port through the adjusting channel, when the system is stopped in an uncontrolled state and the reversing valve core is stopped at the middle position of the valve body so that the pressure input port is not communicated with the two fluid output ports, the pilot mechanism can obtain pressure through the pressure input port through the control mechanism, and then the pilot piston pushes the reversing valve core to move, and the system can be started again.
The automatic control switching straight-path reciprocating power device provided by the invention is matched with the straight-path reciprocating power device by utilizing the fluid flow direction switching valve provided by the invention, the pilot mechanism of the fluid flow direction switching valve obtains a pilot fluid source through the pilot fluid output hole formed in the cylinder barrel of the straight-path reciprocating power device, the pilot fluid source is output to the fluid flow direction switching valve provided by the invention through the pilot fluid output hole, the corresponding pilot mechanism of the fluid flow direction switching valve pushes the reversing valve core to move under the action of the pilot fluid source to realize reversing, a mechanical reversing device is not needed to be arranged in the straight-path reciprocating power device in the whole process, and the piston has no mechanical collision during reversing, small noise and long service life. The automatic control switching straight stroke reciprocating power device provided by the invention realizes automatic reversing operation through position change in the moving process of the piston, and does not need to add other control valves or reversing valves to assist reversing.
The automatic control switching straight-stroke reciprocating power device provided by the invention can be started in a low-pressure state, so that the output pressure adjustable range of the device is wider, and the device is suitable for the working conditions of pressurizing and maintaining pressure of media (fluid) and is also suitable for conveying the media (fluid).
Drawings
Fig. 1 is a schematic view showing the structure of an embodiment 1 of a fluid flow direction switching valve of the present invention.
Fig. 2 is a schematic structural view of the pilot mechanism in fig. 1.
Fig. 3 is a schematic structural view of embodiment 2 of the fluid flow direction switching valve of the present invention.
Fig. 4 is a schematic structural view of the pilot mechanism provided with the control mechanism in fig. 3.
Fig. 5 is a partial enlarged view of the portion C in fig. 4.
Fig. 6 is a schematic view of another view of embodiment 2 of the fluid flow direction switching valve of the present invention.
Fig. 7 is a schematic structural view of embodiment 3 of the fluid flow direction switching valve of the present invention.
Fig. 8 is a schematic view of another view of embodiment 3 of the fluid flow direction switching valve of the present invention.
Fig. 9 is a schematic structural view of embodiment 4 of the fluid flow direction switching valve of the present invention.
Fig. 10 is a schematic diagram of the structure of the automatic control switching straight stroke reciprocating power device of the present invention.
Fig. 11 is a schematic view of the structure of the automatic control switching straight stroke reciprocating power apparatus of the present invention in another state.
Fig. 12 and 13 are schematic structural views of an embodiment of a check valve in the pilot mechanism.
Wherein: 100 fluid flow direction switching valve, 1 valve body, 2 valve cavity, 3 reversing valve core, 4 pilot mechanism, 4-1 pilot chamber housing, 4-1-1 pilot chamber end cap, 4-1-2 pilot chamber main housing, 4-2 pilot chamber, 4-2-1 outer chamber, 4-2-2 inner chamber, 4-3 pilot piston, 4-4 screw, 4-5 check valve, 4-5-2 sealing ring, 4-5-3 check valve stem, 4-5-4 spring, 4-5-5 steel ball, 4-5-6 check valve core, 4-6 adjusting screw, 4-7 mounting hole plug, 4-8 sealing ring, 4-9 duct one, 4-10 control button, 4-11 pilot valve core, 4-12 fluid nozzle, 4-13 fluid outlet, 4-14 pilot valve seat, 4-15 valve core return spring, 4-16 through hole, 4-17 spool mounting hole, 4-18 check valve mounting hole, 5 two, P pressure input port, a second fluid output port, B second fluid output port, R second fluid output port, second fluid return port, second fluid input port, second fluid drain port, first fluid drain port and second fluid drain port;
200 straight-travel reciprocating power cylinder body, 6 cylinder, 7 front end cover, 8 rear end cover, 9 piston cavity, 9-1 front piston cavity, 9-2 rear piston cavity, 10 piston, 11 piston rod, M central line, F first pilot fluid output hole, V second pilot fluid output hole, Q front fluid inlet and outlet, H rear fluid inlet and outlet.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be clearly and completely described in connection with the following specific embodiments. Where the terms "center", "vertical", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "first", "second", etc., refer to an orientation or a positional or a sequence relationship based on the orientation or positional relationship shown in the drawings, it is merely for convenience of describing the present invention and simplifying the description, and does not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Example 1
The fluid flow direction switching valve shown in fig. 1 is a two-position five-way reversing valve, and comprises a valve body 1, a valve cavity 2 formed in the valve body 1, a reversing valve core 3 slidably arranged in the valve cavity 2, and guide mechanisms respectively arranged at the left side and the right side of the valve body 1, wherein five valve ports are respectively arranged on the valve body 1, and the five valve ports are respectively a pressure input port P (P or P port for short), a first fluid output port a (a or a port for short), a second fluid output port B (B or B port for short), a first fluid return port R (R or R port for short), and a second fluid return port S (S or S port for short). The port A and the port B can be threaded holes, smooth holes or cylindrical counter bores.
As shown in fig. 1 and 2, the pilot mechanism comprises a pilot chamber housing 4-1, a pilot chamber 4-2 formed in the pilot chamber housing 4-1, and a pilot piston 4-3 arranged in the pilot chamber 4-2, wherein two sides of the valve cavity 2 are communicated, so that two ends of the reversing valve core 3 are respectively communicated with the pilot mechanisms on two sides, and the pilot piston 4-3 is used for pushing the reversing valve core 3 to move to implement reversing. The pilot piston 4-3 is provided with a sealing ring 4-8 on the periphery, the pilot piston 4-3 divides the pilot chamber 4-2 into an outer chamber 4-2-1 and an inner chamber 4-2-2, the inner chamber 4-2 is positioned at one side of the reversing valve core 3, and the outer chamber 4-2-1 is positioned at one side of the pilot mechanism; the pilot chamber shell 4-1 is provided with a pilot fluid inlet and a fluid pressure discharge hole which are communicated with the outer chamber 4-2-1, and a one-way valve 4-5 is arranged on the inner or outer air path of the pilot fluid inlet. In this embodiment, the check valve 4-5 is disposed in the internal air path of the pilot fluid inlet, and the check valve 4-5 is integrated in the pilot chamber housing 4-1. A rubber gasket is arranged between the pilot chamber shell 4-1 and the valve body 1, and the pilot chamber shell can also be sealed by a 0-shaped ring.
As shown in fig. 1 and 2, the pilot fluid inlet of the pilot mechanism on the left side is defined as a first pilot fluid inlet Y (abbreviated as Y or Y port), and the fluid discharge pressure hole is defined as a first fluid discharge pressure hole W (abbreviated as W or W port); the pilot fluid inlet of the pilot mechanism on the right side is defined as a second pilot fluid inlet Z (abbreviated as Z or Z port), and the fluid discharge pressure hole is defined as a second fluid discharge pressure hole U (abbreviated as U or U port). The first pilot fluid inlet Y and the second pilot fluid inlet Z can be in the forms of screw holes, unthreaded holes or cylindrical counter bores.
In this embodiment, the pilot mechanisms on the left and right sides have the same structure. As shown in fig. 2, the pilot chamber housing 4-1 is fixedly provided to the valve body 1 by a screw 4-4, taking a left pilot mechanism as an example. The pilot chamber housing 4-1 is provided with a through hole penetrating up and down at an end portion thereof, the upper portion of the through hole is the first pilot fluid inlet Y, and the lower portion thereof is a check valve mounting hole 4-18 for mounting the check valve 4-5. The first pilot fluid inlet Y is communicated with the check valve mounting hole 4-18 through a small pore with smaller diameter, namely, a step is formed at the joint of the top end of the check valve mounting hole 4-18 and the first pilot fluid inlet Y.
The one-way valve 4-5 comprises a one-way valve rod 4-5-3 arranged in the one-way valve mounting hole 4-18, a sealing ring 4-5-2 is arranged on the top of the one-way valve rod 4-5-3, the one-way valve rod 4-5-3 and the sealing ring 4-5-2 are used for sealing the first pilot fluid inlet Y from the inside, a spring 4-5-4 is sleeved on the one-way valve rod 4-5-3, a cylindrical adjusting screw 4-6 is arranged in the one-way valve mounting hole 4-18, the spring 4-5-4 is arranged between the adjusting screw 4-6 and the one-way valve rod 4-5-3, the adjusting screw 4-6 is matched with the one-way valve mounting hole 4-18 through threads, and a mounting hole plug 4-7 is arranged at the outermost end of the one-way valve mounting hole 4-18. The spring 4-5-4 is used for enabling the one-way valve rod 4-5-3 to prop against the joint of the top end of the one-way valve mounting hole 4-18 and the first pilot fluid inlet Y in a static state, enabling the first pilot fluid inlet Y to be in a closed state, enabling the one-way valve 4-5 not to be opened under the internal pressure, pushing the one-way valve rod 4-5-3 to move downwards under the action of pilot fluid when pilot fluid with a certain pressure enters from the first pilot fluid inlet Y, enabling the first pilot fluid inlet Y to be opened, enabling the spring 4-5-4 to be further compressed at the moment, enabling the one-way valve rod 4-5-3 to move upwards to reset under the action of the spring 4-5-4 when the pilot fluid disappears, and enabling the first pilot fluid inlet Y to be closed.
The pressure of the spring 4-5-4 can be adjusted by screwing the adjusting screw 4-6 at the position of the regulator in the one-way valve mounting hole 4-18, so that the pressure of the one-way valve 4-5 can be adjusted, the lowest reversing pressure of the pneumatic control valve reaches the preset pressure, for example, 0.15MPa, and then the pressure which is greater than or equal to 0.15MPa is obtained at the pilot fluid inlet, so that the whole one-way valve 4-5 can be pushed to be opened, and the fluid flow direction switching valve can be switched. The side wall of the pilot chamber shell 4-1 of the pilot mechanism on the left side is provided with the first fluid pressure discharge hole W, and the first fluid pressure discharge hole W is communicated with the one-way valve mounting hole 4-18 and then communicated with the outer chamber 4-2-1. As another embodiment, the first fluid pressure discharge hole W and the second fluid pressure discharge hole U may be provided on the mounting hole stopper 4-7, or other positions.
As shown in fig. 12 and 13, as an equivalent alternative, the check valve stem 4-5-3 in the check valve 4-5 is interchangeable with the ball 4-5-5 shown in fig. 12 and the check valve core 4-5-6 shown in fig. 13.
Since the right-side pilot mechanism is identical to the left-side pilot mechanism in structure, only the second pilot fluid inlet Z and the second fluid discharge hole U are distinguished in terms of names and reference numerals in order to facilitate the detailed description of the operation process later.
The pressure source fluid is taken as gas to be expressed as a specific embodiment, the fluid flow direction switching valve is described in the embodiment, when the valve works, the first pilot fluid inlet Y is in gas flow, the left pilot piston 4-3 is pushed to move rightwards, at the moment, the first fluid pressure discharge hole W discharges a certain amount of gas, but compared with the air inflow of the first pilot fluid inlet Y, the first fluid pressure discharge hole W discharges a small amount of gas, the movement of the pilot piston 4-3 is not influenced, so that the reversing valve core 3 is pushed to move rightwards by the left pilot piston 4-3, in the process, the second pilot fluid inlet Z is closed, and in the process of being pushed to move rightwards by the reversing valve core 3, the gas in the outer cavity on the right side is discharged from the second fluid pressure discharge hole U. The reversing valve core 3 achieves reversing when moving to the right. And when the second pilot fluid inlet Z is in gas, the pilot piston 4-3 on the right side moves leftwards to push the reversing valve core 3 to move leftwards so as to realize reversing.
The fluid flow direction switching valve operation process described in this embodiment is repeated continuously.
The reversing is carried out by only relying on the first pilot fluid inlet Y and the second pilot fluid inlet Z to alternately generate gas, and other control mechanisms are not required to switch the on-off state and the air flow direction of the first pilot fluid inlet Y and the second pilot fluid inlet Z under the action of the one-way valve and the fluid pressure discharge hole, so that the fluid flow direction switching valve provided by the invention can automatically realize reversing control without electric control or other valve control.
According to the above specific implementation process, the first fluid pressure discharge hole W is used for discharging the fluid in the left pilot chamber 4-2 when the reversing valve core 3 moves leftwards for reversing, so that the left pilot piston 4-3 can smoothly move leftwards, in the process, the left pilot chamber is in pressure relief, and the faster and better the fluid is discharged by the first fluid pressure discharge hole W; when the first pilot fluid inlet Y enters the pilot fluid, the outer chamber of the left pilot chamber 4-2 is acted by the pressure of the entering pilot fluid to push the left pilot piston 4-3 to move rightwards, the left pilot chamber needs to maintain pressure in the process, and the slower the first fluid discharge hole W discharges the fluid better. The same applies to the second fluid discharge hole U. The first fluid discharge pressure hole W and the second fluid discharge pressure hole U are therefore neither larger nor smaller as good. The efficiency of the first fluid pressure discharge hole W and the second fluid pressure discharge hole U for discharging fluid should be considered to satisfy the operation condition in the pressure release and pressure maintaining process of the pilot chamber where the first fluid pressure discharge hole W and the second fluid pressure discharge hole U are located.
When the working pressure of the fluid is higher, the apertures of the first fluid pressure discharge hole W and the second fluid pressure discharge hole U can be increased, and the fluid flow direction switching valve can be kept to finish reversing operation. A compressed air is described as a fluid pressure source, for example, when the input air pressure is 0.15Mpa, the inner diameter of the first pilot fluid inlet Y is 2.5mm, the corresponding inner diameter of the first fluid pressure discharge hole W is 1.8mm, the fluid flow direction switching valve is almost in a critical state capable of completing the reversing operation, and when the input air pressure is increased, the fluid flow direction switching valve can complete the reversing operation, but at this time, the cross section area of the first fluid pressure discharge hole W exceeds 50% of the cross section area of the first pilot fluid inlet Y, so that a great amount of compressed air is lost, and the device is uneconomical to operate. The relationship between the second fluid discharge orifice U and the second pilot fluid inlet Z is the same.
Therefore, as a preferred embodiment, the cross-sectional area of the nominal diameters of the first fluid discharge pressure hole W and the second fluid discharge pressure hole U is 4% to 10%, more preferably 5% to 7%, of the cross-sectional area of the nominal diameters of the first pilot fluid inlet Y and the second pilot fluid inlet Z. For example, the inner diameter of the first fluid discharge hole W corresponding to the inner diameter of the first pilot fluid inlet Y of 2.5mm is preferably 0.5mm to 0.8mm. The relationship between the second fluid discharge orifice U and the second pilot fluid inlet Z is the same.
As an equivalent alternative form, the adjusting mechanism can be arranged at the position of the fluid pressure discharge hole (W, U) for adjusting the opening degree of the fluid pressure discharge hole, and the opening degree of the fluid pressure discharge hole can be adjusted through the adjusting mechanism under different working conditions so that the fluid flow direction switching valve can smoothly finish the switching operation without causing a large amount of energy consumption.
Example 2
Another embodiment of a fluid flow direction switching valve is shown in fig. 3-6.
In this embodiment, a control mechanism for forced start of forced commutation is provided in the pilot mechanism on the right side in addition to embodiment 1. Specifically, the outer chamber of the pilot mechanism on the right side is communicated with the pressure input port P through a regulating channel, and a control mechanism for controlling the on-off of the regulating channel is arranged on the pilot mechanism.
The control mechanism comprises a control button 4-10 arranged on a pilot chamber shell 4-1 of the pilot mechanism and a pilot valve core 4-11 arranged in the pilot chamber shell 4-1 of the pilot mechanism, wherein the pilot valve core 4-11 closes the adjusting channel in a static state, and the control button 4-10 is pressed down to move the pilot valve core 4-11 and then open the adjusting channel. The stationary state described in this embodiment specifically refers to a state in which the pilot mechanism is not subjected to other external forces.
The pilot chamber housing 4-1 of the pilot mechanism provided with the control mechanism comprises a pilot chamber main housing 4-1-2 and a pilot chamber end cover 4-1-1, and the pilot chamber end cover 4-1-1 and the pilot chamber main housing 4-1-2 are fixedly arranged on the valve body 1 through screws 4-4.
In this embodiment, the pilot mechanism on the left and right sides further includes a check valve 4-5 provided in the pilot housing 4-1. In the pilot mechanism provided with the control mechanism, the one-way valve 4-5 is arranged in the pilot chamber end cover 4-1-1, and the specific arrangement structure of the two one-way valves 4-5 is the same as that of the embodiment 1.
The pilot chamber 4-2 is arranged in the pilot chamber main housing 4-1-2, the pilot fluid inlet Z is arranged on the pilot chamber end cover 4-1-1, valve core mounting holes 4-17 are arranged in the pilot chamber main housing 4-1-2 and the pilot chamber end cover 4-1-1, the pilot valve core 4-11 and the pilot valve core seat 4-14 are arranged in the valve core mounting holes 4-17, the pilot chamber housing 4-1 is divided into the pilot chamber main housing 4-1-2 and the pilot chamber end cover 4-1, and the valve core mounting holes 4-17 for mounting the pilot valve core 4-11 are arranged between the pilot chamber main housing 4-1 and the pilot chamber end cover 4-1, so that the pilot valve core 4-11 and the pilot valve core seat 4-14 are convenient to assemble.
The control button 4-10 is arranged on the pilot chamber main shell 4-1-2, a reset spring is sleeved on the control button 4-10, the reset spring enables the control button 4-10 to keep an outwards sprung state, when the control button 4-10 is pressed downwards, the control button 4-10 moves downwards to enable the reset spring to be extruded, and the reset spring enables the control button 4-10 to keep an upwards sprung state under the condition of not being subjected to other external forces.
The fluid nozzle 4-12 and the pilot valve core seat 4-14 are fixedly arranged in the pilot chamber shell 4-1 of the pilot mechanism provided with the control mechanism. Specifically, an outer wall plate is provided on the outer side of the pilot chamber 4-2, and the outer wall plate separates the pilot chamber 4-2 from the spool mounting hole 4-17. The fluid nozzle 4-12 is arranged in the pilot chamber main shell 4-1-2, specifically, the fluid nozzle 4-12 is in a frustum shape and is formed on the outer wall plate, the axis of the fluid nozzle 4-12 is provided with a fluid outlet 4-13, the fluid outlet 4-13 is a blind hole, one end of the fluid outlet 4-13 is communicated with the valve core mounting hole 4-17, and the other end of the fluid outlet is closed. The end of the regulating passage communicates with the fluid outlet 4-13, and the fluid outlet 4-13 communicates with the spool mounting hole 4-17.
The pilot valve core 4-11 is slidably arranged on the pilot valve core seat 4-14, a groove is formed in the pilot valve core 4-11, a boss matched with the groove is arranged on the pilot valve core seat 4-14, and a gap between the pilot valve core seat and the boss can allow fluid to pass through. That is, even though the pilot valve core seat 4-14 and the pilot valve core 4-11 are provided in the valve core mounting hole 4-17, the pilot fluid inlet is still communicated with the pilot chamber 4-2 through the valve core mounting hole 4-17, and the outer wall plate is provided with 2 through holes 4-16 for communicating the valve core mounting hole 4-17 with the pilot chamber 4-2.
A valve core return spring 4-15 is arranged between the pilot valve core 4-11 and the pilot valve core seat 4-14, and the valve core return spring 4-15 enables the pilot valve core 4-11 to seal the fluid outlet 4-13 in a static state. The valve core return spring 4-15 is always in a compressed state, the valve core return spring 4-15 enables the pilot valve core 4-11 to be abutted against the fluid nozzle 4-12 under the condition that other external forces are not applied, and rubber bodies at the end parts of the pilot valve core 4-11 enable the fluid outlet 4-13 to be blocked, so that the adjusting channel is closed. When the control button 4-10 is pressed downwards, the inclined surface at the bottom end of the control button 4-10 pushes the pilot valve core 4-11 to move outwards and away from the fluid nozzle 4-12, so that the fluid outlet 4-13 is opened, the adjusting channel is communicated with the pilot chamber 4-2 through the valve core mounting hole 4-17 and the through hole 4-16, the pressure of the fluid source from the P port enables the pilot piston 4-3 to move, the pushing of the reversing valve core 3 is further achieved, and forced reversing is achieved.
The pilot chamber main shell 4-1-2 is internally provided with a first pore canal 4-9 communicated with the fluid outlet 4-13, the valve body 1 is internally provided with a second pore canal 5 communicated with the pressure input port P, the first pore canal 4-9 is communicated with the second pore canal 5, and the first pore canal 4-9 and the second pore canal 5 form the regulating passage.
As shown in fig. 3, in the present embodiment, a control mechanism is provided in the right pilot mechanism, and a second fluid discharge hole U in the right pilot mechanism is provided in the pilot chamber main casing 4-1-2.
In this embodiment, since the pilot mechanism on the right side is provided with the control mechanism for forced start of forced reversing, if the air source is under low pressure in use, the reversing valve stops and cannot work, and when the air source is restored to normal pressure, if the reversing valve core 3 is just stopped at the middle position of the valve body 1, the port P, the port a and the port B are not communicated, the air source cannot be output through the reversing valve, so that the system cannot be started. Under such a situation, the fluid flow direction switching valve (reversing valve) provided in this embodiment can push the pilot valve core 4-11 to move by pressing the control button 4-10 to open the adjusting channel, at this time, the pilot chamber 4-2 on the right side obtains the pilot air source from the pressure input port P, and the pilot air source pushes the pilot piston 4-3 on the right side to move to the left side, so as to push the reversing valve core 3 to move to the left side to realize the air passage switching of the reversing valve, and the system starts to resume the normal operation after the air passage of the reversing valve is unobstructed. In particular, when the control button 4-10 is pressed, the control button is released immediately after being pressed briefly to reset, and the pressed instant pilot piston 4-3 moves to push the reversing valve core 3 to move and reverse. The pressing time is typically 1-2 seconds.
In the present embodiment, the fluid pressure source is taken as an example, and the same effect can be achieved by using a liquid (e.g., hydraulic oil) as the fluid pressure source under the same principle.
As shown in fig. 3, in the present embodiment, the control mechanism for forced start of forced commutation is provided in the right pilot mechanism, and as an equivalent embodiment, the control mechanism may be provided in the left pilot mechanism, so that the same effect can be achieved.
As shown in fig. 6, two second ducts 5 are symmetrically arranged on the valve body 1, and the left duct is two-way to the left guide mechanism, and the right duct is two-way to the right guide mechanism. The second pore canal on the right side is in butt joint communication with the first pore canal 4-9 in the pilot chamber main shell 4-1-2 of the pilot mechanism on the right side, and an O-shaped sealing ring is arranged at the butt joint position. In the structure shown in fig. 3 in this embodiment, since the left pilot mechanism is not provided with a control mechanism, the second port on the left side has no actual effect, and the second port is sealed at its end by a rubber pad or an O-ring.
In this embodiment, the five valve ports (P, a, B, R, S) are provided at positions shown in fig. 3, the P, R, S being provided on the bottom side, and the a, B being provided on the top side opposite to the bottom side. The two second channels 5 are formed in the manner shown in fig. 6.
When the two products of two embodiments, namely the control mechanism is arranged at one side of the reversing valve and the control mechanisms are arranged at two sides of the reversing valve, are simultaneously produced and processed, the valve bodies of the two products can be completely universal, and the difference is only that whether one of the two pore canals needs to be plugged or not, but the links of the valve body production and distribution are completely not needed to be distinguished, so that the management cost of the processing process is greatly saved.
Example 3
As shown in fig. 7 and 8, another embodiment of the fluid flow direction switching valve according to the present invention is shown. The structural configuration of this embodiment is exactly the same as that of embodiment 2, i.e., the pilot mechanism on the left side is not provided with a control mechanism, and the pilot mechanism on the right side is provided with a control mechanism.
The difference between this embodiment and embodiment 2 is that the valve body 1 has a different structure, specifically, five valve ports (P port, a port, B port, R port, S port) are opened at different positions. In this embodiment, as shown in fig. 7, the P port, the R port, and the S port are provided on the bottom surface side, and the a port and the B port are provided on the side surface perpendicular to the bottom surface thereof. In this embodiment, the second orifice 5 is opened in the manner shown in fig. 8 due to the relationship between the positions of the five ports. This valve body principle is also suitable for embodiments 1, 2 and 4.
Example 4
As another embodiment, as shown in fig. 9, control mechanisms for forced starting may be provided on both the left and right sides of the pilot mechanism, and referring to fig. 3, the structure of this example is such that the pilot mechanism on the left side shown in fig. 3 is replaced with the pilot mechanism on the right side, and a second orifice 5 is also provided on the left side of the valve body 1. Therefore, the pilot mechanisms at the left side and the right side are provided with control mechanisms for forced starting, and when the working condition that the pilot mechanisms cannot be started for the second time after low-pressure shutdown is met, one of the control buttons 4-10 is pressed at will, so that the second starting can be realized. The two control buttons 4-10 provide greater convenience, and any pressing of one of the control buttons 4-10 in the normal state may effect a restart, and if the desired restart effect cannot be achieved when one of the control buttons is pressed in the uncontrolled condition, the other control button may be selected to be pressed.
The structure of the valve body 1 in this embodiment adopts the structure of the valve body 1 shown in fig. 3 and 6, and is different in that the sealing gasket at the end of the second port 5 on the left side is replaced with an O-shaped sealing ring, so that the second port 5 is opened.
Example 5
Fig. 10 and 11 show an embodiment of an automatic control switching straight stroke reciprocating power device according to the present invention.
The automatic control switching straight-path reciprocating power device described in this embodiment includes the fluid flow direction switching valve 100 described in any one of embodiments 1 to 4, and the straight-path reciprocating power cylinder 200, which may be a cylinder or a hydraulic cylinder, and similarly, a gas reversing valve or a hydraulic reversing valve is used for the corresponding fluid flow direction switching valve. For convenience of description, the present embodiment describes in detail a situation where gas is used as a fluid power source.
As shown in fig. 10 and 11, the fluid flow direction switching valve illustrated in this embodiment adopts the fluid flow direction switching valve described in embodiment 2 or embodiment 3, in which a pilot mechanism on one side is provided with a forced-start control mechanism for forced commutation.
The straight-travel reciprocating power cylinder body comprises a cylinder barrel 6, a front end cover 7 and a rear end cover 8 which are arranged at two ends of the cylinder barrel 6 in a sealing manner, and a piston 10 arranged in the cylinder barrel 6, wherein a piston cavity 9 for accommodating the piston 10 is formed in the cylinder barrel 6, the piston 10 divides the piston cavity 9 into a front piston cavity 9-1 and a rear piston cavity 9-2, a first pilot fluid output hole F (F or F port for short) and a second pilot fluid output hole V (V or V port for short) are arranged on the wall of the cylinder barrel 6, and as a further improvement, the first pilot fluid output hole F and the second pilot fluid output hole V are respectively arranged at two sides of a middle line in the length direction of the cylinder barrel 6; preferably, the first pilot fluid output hole F and the second pilot fluid output hole V are symmetrically arranged with respect to a center line M in the longitudinal direction of the cylinder tube.
The number of the first pilot fluid output holes F and the second pilot fluid output holes V is N, and N is a positive integer greater than or equal to 1. When N is greater than 1, N first pilot fluid output holes F and second pilot fluid output holes V are respectively distributed along the circumferential direction of the cylinder 6. The first pilot fluid output hole F and the second pilot fluid output hole V may be circular holes, kidney-shaped holes or threaded holes, and preferably, the first pilot fluid output hole F and the second pilot fluid output hole V are in communication with the first pilot fluid inlet Y and the second pilot fluid inlet Z of the fluid flow direction switching valve 100 and provide sufficient pilot fluid thereto.
Preferably, the total cross-sectional area of the first pilot fluid output hole F corresponds to the cross-sectional area of the first pilot fluid inlet Y; similarly, the total cross-sectional area of the second pilot fluid outlet hole V corresponds to the cross-sectional area of the second pilot fluid inlet Z.
As shown in fig. 10, when the piston 10 moves to the front end of the cylinder tube 6, the piston 10 closes the second pilot fluid output hole V, and the first pilot fluid output hole F communicates with the rear piston chamber 9-2; as shown in fig. 11, when the piston 10 moves to the rear end of the cylinder tube 6, the piston 10 closes the first pilot fluid output hole F, and the second pilot fluid output hole V communicates with the rear front plug chamber 9-1; when the piston 10 is located in the middle of the cylinder 6, the first pilot fluid output hole F and the second pilot fluid output hole V are both blocked by the piston 10 so as not to communicate with the piston chamber 9. During operation, no position of the piston 10 is where the first pilot fluid output port F and the second pilot fluid output port V are in communication with the piston chamber 9 at the same time.
The front end cover 7 is provided with a front fluid inlet and outlet Q communicated with the front piston cavity 9-1, and the rear end cover 8 is provided with a rear fluid inlet and outlet H communicated with the rear piston cavity 9-2; the front fluid inlet Q (Q or Q port) and the rear fluid inlet H (H or H port) are respectively connected to one fluid outlet on the fluid flow direction switching valve, in this embodiment, the front fluid inlet Q is connected to the first fluid outlet a, and the rear fluid inlet H is connected to the second fluid outlet B.
The first pilot fluid output hole F and the second pilot fluid output hole V are respectively communicated with a pilot fluid inlet of a pilot mechanism on the corresponding side of the fluid flow direction switching valve. In this embodiment, the second pilot fluid output hole V communicates with the second pilot fluid inlet Z, and the first pilot fluid output hole F communicates with the first pilot fluid inlet Y.
The first pilot fluid output hole F and the second pilot fluid output hole V are used for providing pilot air sources for corresponding pilot mechanisms, and under the condition that the pressure and flow of the required pilot air sources are constant, the smaller the aperture is, the smaller the curve formed by the first pilot fluid output hole F and the second pilot fluid output hole V intersecting the cylinder 6 is, so that the damage of the opened holes to the piston 10 in the running process is smaller. The number of the first pilot fluid output holes F and the second pilot fluid output holes V is not only required to consider the influence degree on the smoothness of the inner wall of the cylinder 6, but also the strength of the cylinder 6, so that the strength of the cylinder 6 is not significantly affected by the number of the first pilot fluid output holes F and the second pilot fluid output holes V. Therefore, the number of the first pilot fluid output holes F and the second pilot fluid output holes V is preferably 1 to 4.
The straight-travel reciprocating power cylinder body adopted in the embodiment adopts a cylinder. In this embodiment, fig. 10 and 11 show a rod cylinder, a piston rod 11 is fixedly disposed on the piston 10, the piston rod 11 passes through the front end cover 7 and extends out of the piston cavity 9, and a sealing mechanism is disposed between the piston rod 11 and the front end cover 7.
In order to avoid the piston 10 from striking the front end cover 7 and the rear end cover 8 before reversing, when the piston 10 moves to the front end of the cylinder tube 6 to enable the first pilot fluid output hole F to be communicated with the rear piston cavity 9-2, a buffer gap exists between the front end of the piston 10 and the front end cover 7; when the piston 10 moves to the rear end of the cylinder tube 6 to enable the second pilot fluid output hole V to be communicated with the rear front plug cavity 9-1, a buffer gap exists between the rear end of the piston 10 and the rear end cover 8.
The operation of the automatic control switching straight stroke reciprocating power apparatus according to the present embodiment will be described in detail with reference to fig. 10 and 11.
The gas in the pilot chamber on the right side of the initial setting is discharged through the second fluid pressure discharge hole U, and the port P is communicated with the port A. Compressed gas enters the front piston chamber 9-1 in the cylinder 6 through P-a-Q, the piston 10 moves to the right, and gas in the rear piston chamber 9-2 is discharged through H-B-S. Until the piston 10 passes through the second pilot fluid output hole V, i.e., Q-V-Z pass (as shown in fig. 11), the Z port is charged, the compressed air enters the outer chamber of the pilot mechanism on the right side, and at this time, a part of the gas from the pilot gas source entering through the Z port flows out through the U port, but the pushing of the pilot piston 4-3 on the right side is not affected because the U port is smaller. The compressed air pushes the pilot piston 4-3 on the right side to move leftwards, and pushes the reversing valve core 3 to move leftwards. The reversing valve core 3 pushes the left pilot piston 4-3 to synchronously move leftwards, and air in the left pilot chamber is discharged through the W port. At this time, the reversing valve core 3 finishes the complete reversing instantaneously, that is, the reversing valve core is at the leftmost limit position, at this time, the port P is the same as the port B, the compressed air enters the cylinder 6 through the port P-B-H, the piston 10 moves leftwards, and the gas in the front piston cavity 9-1 is discharged through the port Q-A-R. Until the piston 10 passes through the first pilot fluid output hole F, i.e., the H-F-Y port (as shown in fig. 10), the Y port is charged, the compressed air enters the outer chamber of the left pilot mechanism, and at this time, a part of the gas from the pilot gas source entering through the Y port flows out through the W port, but the pushing of the left pilot piston is not affected because the W port is smaller. The compressed air pushes the left pilot piston to move rightwards, and drives the reversing valve core to move rightwards. The reversing valve core pushes the pilot piston on the right side to synchronously move rightward, and air in the pilot chamber on the right side is discharged through the U-shaped port. At this time, the reversing valve core moves to the rightmost side to complete the complete reversing. At this time, the port P communicates with the port A, compressed air enters the front piston chamber 9-1 in the cylinder 6 through the port P-A-Q (returns to the original setting), the piston 10 moves rightward, and gas in the rear piston chamber 9-2 is discharged through the port H-B-S. And continuously repeating the circulating process to realize automatic control and switching of the reciprocating operation of the straight-stroke reciprocating power device.
In the reciprocating operation process of the automatic control switching straight-stroke reciprocating power device provided by the invention, the pilot gas sources of the pilot mechanisms on the left side and the right side of the fluid flow direction switching valve 100 are taken from the V port and the F port which are arranged on the cylinder 6, and the V port and the F port are alternately opened to obtain the gas source in the piston cavity 9 along with the movement of the piston 10, so that the corresponding pilot mechanisms obtain the pilot gas sources, and then the fluid flow direction switching valve 100 performs reversing operation. In this process, no mechanical reversing device is arranged in the straight-travel reciprocating power cylinder 200, and no mechanism such as an electromagnetic valve is arranged on the gas path of the prior gas guide source to switch the gas flow direction, so that the automatic control switching straight-travel reciprocating power device provided by the embodiment avoids the impact of the piston on the front end cover and the rear end cover, can reduce the noise generated in the running process of equipment, and can prolong the service life of the device.
In the normal operation state of the device, the control mechanism for the secondary start of the pilot mechanism on the right side is not required to be operated. Therefore, in the above-described process, the structure of the fluid flow direction switching valve 100 described in embodiment 1 can be fully adopted, and the device can be operated normally.
The control mechanism is only activated when the control button 4-10 is forced to be actuated, and the following details the working principle of forced actuation of the button:
it should be noted that when the fluid flow direction switching valve 100 is a pneumatic control valve, the reversing valve core cannot be completely reversed when the input air pressure is low to a certain extent, so that the port P cannot be communicated with the port a or the port B, and the direct-stroke automatic reciprocating cylinder cannot be started for the second time, which is a situation often occurring in the prior art. The fluid flow direction switching valve 100 with the control mechanism provided by the invention can solve the problem that the direct-travel automatic reciprocating cylinder cannot be started secondarily because the reversing valve core cannot be completely reversed due to too low pressure.
The function of the control mechanism in the case where the fluid flow direction switching valve 100 with the control mechanism described in embodiments 2 and 3 cannot be activated twice after the low pressure stop is described below using the piston 10 at three different positions in the straight-path reciprocating power cylinder 200, i.e., at the front end cap limit position, the rear end cap limit position, and the intermediate position.
As shown in fig. 10, when the piston 10 is at the limit position on the front end cover 7 side of the straight-stroke reciprocating power cylinder 200, the port P may communicate with the pilot chamber on the right side through the control button on the right side. In this state, when the secondary start-up after the shutdown is performed, it is noted that the idle load can be started up as follows when the pressure of the intake air source is 0.15MPa or more. If loaded, the higher the viscosity, the higher the activation pressure, depending on the viscosity of the medium. The barometer can be observed according to the actual working pressure, and when the air source pressure reaches the working pressure, the operation is started.
The specific operation mode is as follows: the control button 4-10 on the right is pressed, and care should be taken when pressing, and the control button is released instantaneously after pressing. At this time, the right pilot valve core moves rightwards, compressed air enters into the outer cavity of the right pilot cavity from the P port through the adjusting channel, and because of the sealing of the one-way valve, gas cannot flow out along the Z port, but a part of gas is discharged through the U port, and the U port is provided with a reasonable aperture or a damping mechanism, so that the displacement of the damping mechanism cannot influence the movement of the pilot piston. The compressed air pushes a pilot piston in the right pilot mechanism to move leftwards, and then pushes the reversing valve core to move leftwards. The reversing valve core pushes the left pilot piston to synchronously move leftwards, air in the left pilot cavity is discharged through the W port, the reversing valve core is completely reversed instantaneously, namely the reversing valve core is positioned at the leftmost limit position, at the moment, the P port and the B port are communicated, and compressed air passes through the P-B-H port to the rear piston cavity in the cylinder barrel and then passes through the F port to the Y port. And the gas enters the left pilot cavity through the Y port, and part of the gas is discharged through the W port, so that the W port is provided with a reasonable aperture or a damping mechanism, and the displacement of the damping mechanism can not influence the movement of the pilot piston. The pilot air flow pushes the left pilot piston to move rightwards and pushes the reversing valve core to move rightwards. The reversing valve core pushes the pilot piston on the right side to synchronously move rightward, and air in the pilot cavity on the right side is discharged through the U port. At this time, the reversing valve core instantaneously completes complete reversing, that is, the valve core is at the extreme right position.
And when the reversing valve core is positioned at the extreme position of the rightmost side, reversing is completed, and the port P is communicated with the port A. Compressed air enters the front piston cavity 9-1 in the cylinder 6 through the P-A-Q, the compressed air pushes the piston 10 to move rightwards, and the air in the rear piston cavity 9-2 is discharged through the H-B-S. Until the piston moves to the right of the V port, the V port is communicated with the front piston chamber 9-1, i.e., Q-V-Z, the Z port is charged, the compressed gas enters the outer chamber of the right pilot mechanism, and at this time, a part of the gas is discharged through the U port. The compressed air pushes the pilot piston on the right side to move leftwards, and the pilot piston pushes the reversing valve core to move leftwards. The reversing valve core pushes the left pilot piston to synchronously move leftwards, and air in the left pilot cavity is discharged through the W port. At this time, the valve core finishes the complete reversing instantly, namely the reversing valve core is positioned at the leftmost limit position. The port P is communicated with the port B, compressed air enters the rear piston cavity 9-2 in the cylinder barrel 6 through P-B-H, the piston 10 moves leftwards, and gas in the front piston cavity 9-1 is discharged through Q-A-R. Until the piston 10 passes through port F, i.e., port H-F-Y, the port Y is charged and compressed gas enters the outer chamber of the left pilot mechanism, at which point a portion of the gas is expelled through port W. The compressed air pushes the left pilot piston to move rightwards and pushes the reversing valve core to move rightwards. The reversing valve core pushes the pilot piston on the right side to synchronously move rightward, and air in the pilot cavity on the right side is discharged through the U port. At this time, the reversing valve core instantly completes complete reversing, namely after the reversing valve core is at the extreme right position, the port P is communicated with the port A, compressed air enters the front piston cavity in the cylinder barrel through the port P-A-Q, the piston 10 moves rightwards, and gas in the rear piston cavity is discharged through the port H-B-S. Under the condition that the air source pressure is stable, the device can continuously repeat the process, and automatic reciprocating motion is realized.
Therefore, when the fluid flow direction switching valve 100 cannot be started for the second time after the low pressure is stopped, the port a and the port B cannot be communicated with the port P, so that the fluid flow direction switching valve cannot be started again, but the control button 4-10 in the fluid flow direction switching valve 100 is pressed by the automatic control switching straight stroke reciprocating power device provided by the embodiment, a pilot air source signal can be obtained from the port P for a pilot mechanism, and further, the pilot piston of the pilot mechanism pushes the reversing valve core to move to realize reversing, so that the port P and the port a or the port B realize communicating and continuous reversing actions, realize automatic reciprocating motion, and finish the second starting.
The pressing time is not too long to exceed the single stroke time of the piston 10 when the control button is pressed. If the control button is not released instantaneously, the left and right pilot chambers are filled with pressurized gas, the pressures at the two sides counteract, and the left and right pilot pistons cannot push the reversing valve core to realize reversing.
As shown in fig. 11, when the piston 11 is at the limit position of the rear end cap of the straight-stroke reciprocating power cylinder 200, the specific implementation process of the secondary start is as follows, and since the working principle of each part in the device is the same as that of the previous process, the repeated parts in the following description will not be repeated.
When the control button 4-10 of the right pilot mechanism is started, at the moment, the right pilot valve core moves rightwards, so that the regulating channel is opened, compressed air enters into the outer cavity of the right pilot mechanism from the P port through the regulating channel (the structure and principle of the control button are shown in the embodiment 2), the compressed air pushes the right pilot piston to move leftwards, the reversing valve core is pushed to move leftwards, the reversing valve core pushes the left pilot piston to synchronously move leftwards along with the control button, and then the valve core completes complete reversing thoroughly, namely the reversing valve core is positioned at the leftmost limit position. The P port is communicated with the B port. Compressed air enters the rear piston cavity in the cylinder 6 through P-B-H, the piston 10 moves leftwards, and then the working process of each part is the same as that of the previous process, and the device is started for the second time at the moment, and normal reciprocating motion is recovered.
The following is a specific implementation of the piston 10 at the time of the secondary start at the time of the intermediate position (not shown in the drawing) of the straight stroke reciprocating power cylinder 200.
When the hydraulic reversing valve is started, the right control button is pressed, at the moment, the right pilot valve core moves rightwards, compressed air enters into the outer cavity of the right pilot cavity from the port P, the piston of the right pilot cavity is pushed to move leftwards by the compressed air, the reversing valve core is pushed to move leftwards, the left pilot piston is pushed to synchronously move leftwards by the reversing valve core along with the left pilot valve core, the reversing valve core instantly completes complete reversing, at the moment, the reversing valve core is at the leftmost limit position, and the port P is communicated with the port B. Compressed air enters the right cavity of the cylinder through P-B-H, the piston 10 moves leftwards, and the air in the piston cavity is discharged through Q-A-R. The working process of each component is the same as the previous process, and the device realizes secondary starting and resumes normal reciprocating motion.
When the piston is at different positions in front, middle and back, the right pilot mechanism is pressed to obtain a pilot air source from the port P, so that the reversing valve core is pushed to move leftwards to realize reversing, the port P is communicated with the port B, and the subsequent device can realize normal reciprocating motion. Similarly, when the control mechanism is provided on the left side, the above-described secondary start can be achieved.
In this embodiment, for convenience in illustrating the gas path connection principle of the device, the gas path line is illustrated by a dotted line. In practical products, only the inlet pipe of the P port is usually visible, and other air pipes are transmitted through the connecting plate and the bus plate (not shown in the figure).
In the above embodiments, the fluid pressure source is described using compressed air as an example, and the present invention is equally applicable to hydraulic control. When the fluid pressure source adopts hydraulic oil, the straight-stroke reciprocating power cylinder 200 of the execution part is changed into an oil cylinder, and the fluid flow direction switching valve 100 is changed into a valve for hydraulic pressure.
The automatic control switching straight stroke reciprocating power device provided by the invention has no coil and does not need electric control. When the compressed air is used as a power source, the W port and the U port are used for exhausting, the compressed air can be directly exhausted to the atmosphere, and when the hydraulic oil is used as a fluid power source, the hydraulic oil exhausted from the W port and the U port returns to the oil pool.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims (10)

1. A fluid flow direction switching valve, characterized by: the switching valve is a two-position five-way reversing valve and comprises a valve body, a valve cavity formed in the valve body, a reversing valve core arranged in the valve cavity in a sliding manner and a guide mechanism respectively arranged at the left side and the right side of the valve body, wherein five valve ports are arranged on the valve body, and the five valve ports are a pressure input port, two fluid output ports and two fluid reflux ports;
the pilot mechanism comprises a pilot chamber shell, a pilot chamber formed in the pilot chamber shell and a pilot piston arranged in the pilot chamber, wherein the pilot piston is used for pushing the reversing valve core to move and reverse, and the pilot piston divides the pilot chamber into an inner chamber positioned at one side of the reversing valve core and an outer chamber positioned at the other side of the reversing valve core;
The pilot chamber shell is provided with a pilot fluid inlet and a fluid pressure discharge hole which are communicated with the outer chamber, and a one-way valve is arranged on the internal or external air path of the pilot fluid inlet.
2. A fluid flow direction switching valve according to claim 1, wherein: at least one outer chamber of the pilot mechanism is communicated with the pressure input port through a regulating channel, and a control mechanism for controlling the on-off of the regulating channel is arranged on the pilot mechanism.
3. A fluid flow direction switching valve according to claim 2, wherein: the control mechanism comprises a control button arranged on a pilot chamber shell of the pilot mechanism and a pilot valve core arranged in the pilot chamber shell of the pilot mechanism, wherein the pilot valve core closes the regulating channel in a static state, and the control button is pressed down to move the pilot valve core to open the regulating channel.
4. A fluid flow direction switching valve according to claim 3, wherein: the pilot valve is characterized in that a fluid nozzle and a pilot valve core seat are fixedly arranged in a pilot chamber shell of a pilot mechanism of the control mechanism, a fluid outlet is arranged on the fluid nozzle, the tail end of the adjusting channel is communicated with the fluid outlet, the pilot valve core is slidably arranged on the pilot valve core seat, a valve core reset spring is arranged between the pilot valve core and the pilot valve core seat, and the valve core reset spring enables the pilot valve core to seal the fluid outlet in a static state.
5. A fluid flow direction switching valve according to claim 4 wherein: the pilot chamber housing of the pilot mechanism provided with the control mechanism comprises a pilot chamber main housing and a pilot chamber end cover, the pilot chamber is arranged in the pilot chamber main housing, the pilot fluid inlet is arranged on the pilot chamber end cover, valve core mounting holes are formed in the pilot chamber main housing and the pilot chamber end cover, the pilot valve core and the pilot valve core seat are arranged in the valve core mounting holes, the control button is arranged on the pilot chamber main housing, and the fluid nozzle is arranged in the pilot chamber main housing.
6. A fluid flow direction switching valve according to claim 5 wherein: the pilot chamber main shell is internally provided with a first pore canal communicated with the fluid outlet, the valve body is internally provided with a second pore canal communicated with the pressure input port, the first pore canal is communicated with the pore canal, and the first pore canal and the second pore canal form the regulating channel.
7. A fluid flow direction switching valve according to any one of claims 1-6 wherein: the pilot valve is arranged in an internal gas circuit of the pilot fluid inlet, a check valve mounting hole is formed in the pilot chamber shell, the check valve comprises a check valve rod arranged in the check valve mounting hole, a sealing ring is arranged on the top of the check valve rod, the check valve rod and the sealing ring are used for enabling the pilot fluid inlet to be sealed from the inside, a spring is sleeved on the check valve rod, a cylindrical adjusting screw is arranged in the check valve mounting hole, the spring is arranged between the adjusting screw and the check valve rod, and the adjusting screw is in threaded fit with the check valve mounting hole.
8. An automatic control switching straight stroke reciprocating power device is characterized in that: the hydraulic fluid flow direction switching valve comprises a fluid flow direction switching valve and a straight stroke reciprocating power cylinder body as claimed in any one of claims 1 to 7, wherein the straight stroke reciprocating power cylinder body comprises a cylinder barrel, a front end cover and a rear end cover which are arranged at two ends of the cylinder barrel in a sealing manner, and a piston arranged in the cylinder barrel, a piston cavity for accommodating the piston is formed in the cylinder barrel, the piston divides the piston cavity into a front piston cavity and a rear piston cavity, and a first pilot fluid output hole and a second pilot fluid output hole are formed in the wall of the cylinder barrel;
a piston rod is fixedly arranged on the piston, the piston rod penetrates through the front end cover and extends out of the piston cavity, and a sealing mechanism is arranged between the piston rod and the front end cover;
when the piston moves to the front end of the cylinder barrel, the piston seals the second pilot fluid output hole, and the first pilot fluid output hole is communicated with the rear piston cavity;
when the piston moves to the rear end of the cylinder barrel, the piston seals the first pilot fluid output hole, and the second pilot fluid output hole is communicated with the front piston cavity;
The front end cover is provided with a front fluid inlet and a front fluid outlet which are communicated with the front piston cavity, and the rear end cover is provided with a rear fluid inlet and a rear fluid outlet which are communicated with the rear piston cavity;
the front fluid inlet and the rear fluid inlet are respectively communicated with two fluid output ports on the fluid flow direction switching valve, and the first pilot fluid output hole and the second pilot fluid output hole are respectively communicated with a pilot fluid inlet of a pilot mechanism on the corresponding side of the fluid flow direction switching valve.
9. The automatic control switching linear stroke reciprocating power device as claimed in claim 8 wherein: the number of the first pilot fluid output holes and the second pilot fluid output holes is N, and N is a positive integer greater than or equal to 1; the N first pilot fluid output holes and the second pilot fluid output holes are distributed and arranged along the circumferential direction of the cylinder barrel.
10. The automatic control switching linear stroke reciprocating power device as claimed in claim 8 wherein: when the piston moves to the front end of the cylinder barrel to enable the first pilot fluid output hole to be communicated with the rear piston cavity, a buffer gap exists between the front end of the piston and the front end cover;
when the piston moves to the rear end of the cylinder barrel to enable the second pilot fluid output hole to be communicated with the front piston cavity, a buffer gap exists between the rear end of the piston and the rear end cover.
CN202310080991.8A 2023-02-08 2023-02-08 Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device Pending CN116104725A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310080991.8A CN116104725A (en) 2023-02-08 2023-02-08 Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310080991.8A CN116104725A (en) 2023-02-08 2023-02-08 Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device

Publications (1)

Publication Number Publication Date
CN116104725A true CN116104725A (en) 2023-05-12

Family

ID=86263478

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310080991.8A Pending CN116104725A (en) 2023-02-08 2023-02-08 Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device

Country Status (1)

Country Link
CN (1) CN116104725A (en)

Similar Documents

Publication Publication Date Title
KR102497763B1 (en) Flow passage switching unit
JPH08277812A (en) Fluid pressure cylinder
JP2011163466A (en) Decompression switching valve
US9127657B2 (en) Air-driven pump system
CN110036210B (en) Supercharging device
KR102007021B1 (en) Compressed air driven reciprocating piston hydraulic pump
CN102230484A (en) Integrated continuous gas-driving hydraulic force booster
CN110520633B (en) Pressure booster
US11143175B2 (en) Pressure booster and cylinder apparatus provided with same
CN109268253B (en) Reciprocating pump with variable pressure increasing ratio
WO2007117099A1 (en) Hydraulic pressure transformers
CN220748472U (en) Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device
CN214368097U (en) Automatic reversing valve control system capable of switching pneumatic booster pump
CN219220905U (en) Straight stroke reciprocating cylinder
CN116104725A (en) Fluid flow direction switching valve and automatic control switching straight stroke reciprocating power device
US20050013716A1 (en) High-pressure generating device
CN209943015U (en) Booster pump
JP2004340149A (en) Diaphragm pump system
KR20140094325A (en) Bypass device for a main air ventilation of a pressure booster
CN111502945B (en) Booster water pump with variable booster ratio
CN210769173U (en) Booster pump
KR20180057162A (en) Linear fluid pump with differential area piston and built-in valve
JPH029105Y2 (en)
JP2014025354A (en) Air drive type diaphragm pump
JP2005042807A (en) Boost type cylinder device

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination