CN112761825A

CN112761825A - Gas injection valve

Info

Publication number: CN112761825A
Application number: CN202011534097.6A
Authority: CN
Inventors: 黄民备; 何静; 欧阳玲湘; 邓飞; 龙美彪
Original assignee: Nanyuediankong Hengyang Industrial Technology Co ltd
Current assignee: Nanyuediankong Hengyang Industrial Technology Co ltd
Priority date: 2020-12-22
Filing date: 2020-12-22
Publication date: 2021-05-07

Abstract

The invention discloses a fuel gas injection valve which is characterized by comprising an armature component, an electromagnet component, a static valve seat and a shell, wherein the electromagnet component, the armature component and the static valve seat are arranged in the shell from top to bottom; the shell is provided with an air inlet transverse hole, and the static valve seat is provided with an air outlet channel; when the electromagnet component is electrified, the armature component is driven to move upwards, and an air outlet channel on the static valve seat is opened to be communicated with an air inlet transverse hole on the shell for exhausting; when the electromagnet component is not electrified, the armature component overcomes the gas pressure to move downwards under the action of the spring of the armature component, and the gas outlet channel on the static valve seat is closed. Compared with the existing gas injection valve, the gas injection valve can realize the fixed-time and fixed-quantity gas supply of each cylinder, can realize the adjustment of the maximum injection flow, and reduces the situations of gas escape, deteriorated emission, waste and the like caused by the valve overlap angle.

Description

Gas injection valve

Technical Field

The invention relates to the technical field of gas supply systems of gas engines, in particular to a gas injection valve.

Background

The performance of the gas injection valve as a key execution component in a gas supply system of a gas engine has a significant influence on injection characteristics such as injection timing, injection duration, injection mass flow rate and the like. The existing gas engine air supply scheme is that air enters a supercharger generally, the supercharged air is mixed with gas in a gas pipeline in a mixer, then the mixture enters an air inlet channel and an air cylinder, and the working process of the engine is realized through ignition of a spark plug. The defects of the scheme have many problems, for example, in the scavenging process, a part of mixed gas enters an engine exhaust pipe to cause a part of gas waste, and more seriously, the gas can flow backwards in the valve overlap period to cause blasting of the gas inlet and exhaust pipe to cause faults.

Disclosure of Invention

The invention aims to solve the problems of the existing similar products, and develops a gas injection valve product with a new structure. The gas supply mode reduces the situations of gas escape, worsening discharge, waste and the like caused by the overlap angle of the valve.

In order to achieve the purpose of the invention, the technical scheme adopted by the invention is as follows:

a fuel gas injection valve comprises an armature component, an electromagnet component, a static valve seat and a shell, wherein the electromagnet component, the armature component and the static valve seat are arranged in the shell from top to bottom; the shell is provided with an air inlet transverse hole, and the static valve seat is provided with an air outlet channel; the electromagnet part drives the armature part to move upwards when being electrified, and an air outlet channel on the static valve seat is opened to be communicated with an air inlet transverse hole on the shell for exhausting; when the electromagnet component is not electrified, the armature component overcomes the gas pressure to move downwards under the action of the spring of the armature component, and the gas outlet channel on the static valve seat is closed.

In a preferred embodiment of the invention, the static valve seat is made of a plastics material to provide a better seal with the armature assembly.

In a preferred embodiment of the present invention, the electromagnet of the electromagnet member is connected to the housing in a threaded manner, and the maximum injection flow rate of the injection valve can be adjusted by adjusting the tightening depth of the electromagnet member.

In a preferred embodiment of the present invention, a rectangular coil is used between the armature assembly and the housing for guiding.

In a preferred embodiment of the present invention, the rectangular ring is made of a plastic material, which can reduce the friction coefficient.

In a preferred embodiment of the invention, the closing response time of the armature assembly is mainly dependent on the magnitude of the gas pressure and the spring force of the own spring.

By adopting the technical scheme, compared with the existing gas injection valve, the gas injection valve can realize the fixed-time and fixed-quantity gas supply for each cylinder, can realize the adjustment of the maximum injection flow, and reduces the situations of gas escape, deteriorated emission, waste and the like caused by the overlap angle of the valve.

Drawings

Fig. 1 is a schematic view of the structure of the gas injection valve of the present invention.

Fig. 2 is a schematic view of the construction of an armature component of the present invention.

Fig. 3 is a schematic structural view of the static valve seat of the present invention.

Fig. 4 is a schematic structural diagram of the housing of the present invention.

Detailed Description

The structure of the invention is further described in detail with reference to the accompanying drawings as follows:

referring to fig. 1 to 4, the gas injection valve shown in the drawings comprises an armature component 100, an electromagnet component 200, a stationary valve seat 250 and a housing 260, and the specific technical scheme is as follows:

armature assembly 100 generally includes an armature assembly 110, a spring 120, an upper spring seat 130, an O-ring 140, and a rectangular ring 150, armature assembly 110 including an armature 111, and a valve seat 112.

The periphery of the armature 111 is composed of two stages of armature rod sections, namely a first armature rod section 111a and a second armature rod section 111b from top to bottom, the middle of the armature 111 is coaxially provided with two armature central hole sections, namely a first armature central hole section 111c and a second armature central hole section 111d from top to bottom.

The periphery of the movable valve seat 112 is composed of three stages of movable valve seat rod segments, which are a first movable valve seat rod segment 112a, a second movable valve seat rod segment 112b and a third movable valve seat rod segment 112c from top to bottom, respectively, and the lower end surface 112d of the first movable valve seat rod segment 112a is a lower mounting surface of the spring 120. The second movable valve seat rod section 112b is provided with a movable valve seat ring groove 112 e. A blind hole 112f is arranged at the center of the lower end face of the movable valve seat 112, and 6 movable valve seat transverse holes 112g are arranged in the circumferential direction of the third movable valve seat rod section 112 c.

The center of the spring upper seat 130 is provided with three spring upper seat hole sections, which are a first spring upper seat hole section 131, a second spring upper seat hole section 132 and a third spring upper seat hole section 133 from top to bottom. The upper end surface 134 of the third spring upper seat rod section 133 is an upper mounting surface of the spring 120, and a spring upper seat transverse hole 135 is formed in the circumferential direction of the third spring upper seat rod section 133 to ensure air pressure balance.

The electromagnet member 200 includes an electromagnet 210, O-rings 220, 240 (not shown in the figure 240), a wave spring 230;

an electromagnet plug 211 is disposed on the upper portion of the electromagnet 210, and the electromagnet plug 211 is connected to a coil (not shown) in the electromagnet 210. The periphery of the electromagnet 210 is provided with four electromagnet rod sections from top to bottom, namely a first electromagnet rod section 212, a second electromagnet rod section 213, a third electromagnet rod section 214 and a fourth electromagnet rod section 215, the first electromagnet rod section 212 and the third electromagnet rod section 214 are respectively provided with a sealing ring groove for mounting O-

shaped sealing rings

220 and 240, and the first sealing ring groove 216 and the second sealing ring groove 217 are respectively arranged from top to bottom. The second electromagnet rod segment 213 is provided with an external thread, and the step surface 218 between the third electromagnet rod segment 214 and the fourth electromagnet rod segment 215 is used for installing the wave spring 230. The wave spring 230 is a stacked multi-layer wave spring.

The center of the static valve seat 250 is provided with an annular conical air outlet channel 251, the periphery of the static valve seat 250 is provided with three static valve seat rod sections from top to bottom, namely a first static valve seat rod section 252, a second static valve seat rod section 253 and a third static valve seat rod section 254, and the third static valve seat rod section 254 is used for installing an O-shaped sealing ring.

The center of the casing 260 is coaxially provided with eight casing hole sections from top to bottom, namely a first casing hole section 261, a second casing hole section 262, a third casing hole section 263, a fourth casing hole section 264, a fifth casing hole section 265, a sixth casing hole section 266, a seventh casing hole section 267 and an eighth casing hole section 268. An internal thread is provided within the second housing bore section 262. The fifth housing bore section 265 is provided with 6 inlet cross bores 269a, the sixth housing bore section 266 is provided with 8 inlet cross bores 269b, and the eighth housing bore section 268 is an outlet bore. The 8 inlet cross bores 269b in the sixth housing bore section 266 communicate with the 6 valve seat cross bores 112g in the third valve seat stem section 112c of the valve seat 112, and the 6 inlet cross bores 269a in the fifth housing bore section 265 communicate with the sprung seat cross bores 135 in the third sprung seat stem section 133 of the sprung seat 130.

The assembly process of the gas injection valve is as follows:

first, assembling the armature component 100: the spring 120 is coaxially mounted on the first movable valve seat stem section 112a of the movable valve seat 112, and the spring upper seat 130 is also coaxially mounted on the first movable valve seat stem section 112a of the movable valve seat 112, so that the upper end face 134 of the third spring upper seat stem section 133 is in contact with the upper end face of the spring 120. The second armature center bore section 111d of the armature 111 is then pressed onto the first movable valve seat stem section 112a of the movable valve seat 112, so that the lower end face of the armature 111 contacts the lower end face 112d of the first movable valve seat stem section 112a of the movable valve seat 112. The first armature center bore section 111c of armature 111 is a press-fit exhaust bore. The O-ring 140 and the rectangular ring 150 are sequentially fitted into the valve seat groove 112e of the second valve seat stem segment 112b of the valve seat 112.

In a second step, the O-ring 270 is inserted into the third static valve seat stem segment 254 of the static valve seat 250, and then the static valve seat 250 is installed into the seventh housing bore segment 267 of the housing 260. The armature member 100 is housed in the housing 260 such that the lower end face of the armature member 100 contacts the upper end face of the stationary valve seat 250. The wave spring 230 is loaded into the third housing bore section 263 of the housing 260. The first sealing ring groove 216 on the first electromagnet rod section 212 and the second sealing ring groove 217 on the third electromagnet rod section 214 of the electromagnet assembly 200 are respectively sleeved with O-

ring seals

220 and 240. The electromagnet member 200 is then fitted into the housing 260. The electromagnet component 260 is screwed through the external thread on the second electromagnet rod section 213 and the internal thread of the second housing hole section 262, so that the lower end face of the electromagnet component 260 contacts with the upper end face of the spring upper seat 130, and the prepressing amount of the spring 120 and the maximum lift of the armature assembly 110 can be adjusted by adjusting the screwing depth of the electromagnet component 260, thereby adjusting the maximum injection flow of the gas injection valve.

The working process and principle of the invention are as follows:

as shown in fig. 1, the gas enters the gas injection valve through the 6 inlet cross holes 269a in the fifth housing bore section 265 and the 8 inlet cross holes 269b in the sixth housing bore section 266 of the housing 260 and into the interior of the gas injection valve simultaneously into the 6 valve seat cross holes 112g in the third valve seat stem section 112c of the valve seat 112 and the sprung cross holes 135 in the third sprung stem section 133 of the sprung seat 130, thereby ensuring gas pressure balance by adjusting the inlet pressure in the 6 inlet cross holes 269a in the fifth housing bore section 265 and the 8 inlet cross holes 269b in the sixth housing bore section 266.

When the power is not supplied, the acting force of the spring 120 on the armature assembly 110 is vertical downward, and the pressure of the gas pressure in the transverse hole 135 of the upper spring seat on the armature assembly 110 is also vertical downward, so that the lower end face of the armature assembly 110 is always in a state of pressing the upper end face of the static valve seat 250, and the gas outlet channel 251 on the static valve seat 250 is kept in a closed state. The material of static valve seat 250 is plastic to provide a better seal with armature assembly 110.

When the electronic control unit sends a command, the coil of the electromagnet 210 is energized, and the armature assembly 110 moves upward under the action of the electromagnetic force, so that the air outlet channel 251 of the static valve seat 250 is opened. The gas enters the inlet pipe (not shown) through the outlet passage 251 of the static valve seat 250.

During the upward movement of armature assembly 110, the gas pressure experienced by armature assembly 110 approaches equilibrium, primarily being acted upon by spring and electromagnetic forces. When the lower end face 112d of the first movable valve seat rod segment 112a of the movable valve seat 112 contacts with the lower end face of the upper spring seat 130, the armature assembly 110 reaches the maximum lift, and at this time, a certain distance is left between the upper end face of the armature 111 and the lower end face of the electromagnet component 200, and the upper end face of the armature 111 is subjected to gas pressure (the gas pressure enters from the transverse spring seat hole 135, a gap between the lower end face of the armature 111 and the lower end face 112d of the first movable valve seat rod segment 112a, a gap between the first movable valve seat rod segment 112a and the second armature center hole segment 111d, and the first armature center hole segment 111 c). At maximum lift, armature assembly 110 is exposed to upward gas pressure, which is primarily dependent on the gas pressure and the area of the lower end surface of lower spring seat 130. The opening response time depends mainly on the magnitude of the electromagnetic force, the gas pressure and the spring force.

When the oil injection pulse width meets the requirement, the electromagnet 210 cuts off the current of the coil of the electromagnet 210 under the instruction of the electronic control unit, and the electromagnetic force is removed. Armature assembly 110 is also subjected to upward gas pressure and a downward spring force. When the gas pressure is less than the spring force, armature assembly 110 begins to move downward. During the downward movement of armature assembly 110, the gas pressures approximately balance each other, and the resultant force is only the downward spring force. The spring force quickly seats armature assembly 110 and the gas supply is complete. The closing response time of armature assembly 110 is primarily dependent on the magnitude of the gas pressure and the spring force. Rectangular ring 150 provides a guide during up and down movement of armature assembly 110. Because the gas has no lubrication function, the dry friction coefficient between metals is large, and the friction coefficient can be reduced by adopting the rectangular ring 150 made of special materials such as plastics for guiding.

Claims

1. A fuel gas injection valve is characterized by comprising an armature component, an electromagnet component, a static valve seat and a shell, wherein the electromagnet component, the armature component and the static valve seat are arranged in the shell from top to bottom; the shell is provided with an air inlet transverse hole, and the static valve seat is provided with an air outlet channel; when the electromagnet component is electrified, the armature component is driven to move upwards, and an air outlet channel on the static valve seat is opened to be communicated with an air inlet transverse hole on the shell for exhausting; when the electromagnet component is not electrified, the armature component overcomes the gas pressure to move downwards under the action of the spring of the armature component, and the gas outlet channel on the static valve seat is closed.

2. A gas injection valve according to claim 1, wherein said static valve seat is formed of a plastics material to provide a better seal with said armature assembly.

3. The gas injection valve of claim 1 wherein said solenoid of said solenoid assembly is threadably connected to said housing, and wherein the maximum injection flow rate of said injection valve is adjustable by adjusting the depth to which said solenoid assembly is tightened.

4. A gas injection valve according to claim 1, wherein a rectangular ring is used between said armature assembly and said housing for guidance.

5. A gas injection valve according to claim 4, wherein said rectangular ring is made of a plastic material and serves to reduce the coefficient of friction.

6. A gas injection valve according to any one of claims 1 to 5 wherein the closing response time of said armature assembly is dependent primarily on the magnitude of the gas pressure and the spring force of the own spring.