WO2013174303A1

WO2013174303A1 - Balancing sealing valve and valve system using the same

Info

Publication number: WO2013174303A1
Application number: PCT/CN2013/076213
Authority: WO
Inventors: 姚其槐; 姚镇
Original assignee: 北京星旋世纪科技有限公司
Priority date: 2012-05-24
Filing date: 2013-05-24
Publication date: 2013-11-28
Also published as: CN103422929B; CN103422929A

Abstract

A balancing sealing valve and a valve system including the balancing sealing valve is provided, pistons (320,340) are each provided at the upper and lower sides of an inlet of the balancing sealing valve. According to Pascal's principle, the pressures upon two pistons are counteracted. Thereby the sealing valve is reliably closed when the gas in an inlet conduit (12) is the compressed gas. And within the frequent reliable opening and closing actions, only a small force can be needed to flexibly drive the valve.

Description

Balancing sealing valve and valve system using the same

The invention relates to the technical field of fluid sealing valves in the mechanical industry, and in particular to a balanced sealing valve and a valve system using the same. Background technique

As we all know, the traditional four-stroke reciprocating piston engine "gas timing" refers to the position of the piston in the cylinder when the intake and exhaust valves are opened and closed, that is, the crank angle of the piston before and after the upper and lower dead ends. The forward and exhaust continuous angles are determined experimentally and are strictly defined during the manufacture of the engine. This task is accomplished by the associated positioning drive of the crankshaft timing gear and the valve camshaft gear. In order to make the combustible mixture sucked into the cylinder burn rapidly to generate a large pressure, so that the engine emits a large amount of power, the combustible mixed gas must be compressed before combustion to reduce the volume, increase the density, and increase the temperature. That is, the compression process is required, and the pressure of the mixture will increase to 0.6-1.2 MPa and the temperature can reach 600-700K. There is a very important concept in this itinerary, the compression ratio. The so-called compression ratio is the ratio of the maximum volume of gas in the cylinder before compression to the minimum volume after compression. Generally, the larger the compression ratio, the higher the pressure and temperature of the mixture at the end of compression, and the faster the combustion speed, so the greater the power emitted by the engine, the better the economy. The compression ratio of a typical family car is between 8 and 10. With the call for energy conservation and environmental protection, in order to achieve combustion under lean oil gas, it is necessary to pursue a so-called high air-fuel ratio that is closely related to the compression ratio. If the light relies on the suction and compression strokes of the cylinder, the aforementioned compression ratio cannot meet the requirements of fuel economy and high air-fuel ratio. There is a direct-injection engine, such as the German Halls (SKS) combustion system. A method of directly injecting pressurized gas into the cylinder is employed. Regardless of which of the above two methods, it is necessary to solve the valve opening and closing problem in which the pressurized gas enters the combustion chamber.

1 is a schematic cross-sectional view of a prior art engine piston cylinder valve system. As shown in FIG. 1, the cylinder block 1 encloses a piston space, and the valve system is disposed on the cylinder head 5. The piston 2 can move up and down in the piston space, and an exhaust sealing valve 4 is disposed at the boundary between the piston space and the exhaust passage 11. An injector 10 is disposed on the upper wall of the intake passage 12, and an intake sealing valve 3 is disposed at a boundary between the piston space and the intake passage 12. The intake sealing valve 3 and the exhaust sealing valve 4 are each formed into a bell shape, and the cam In the mechanism, the cam 9 rotates around its camshaft, one end of the tappet 8 is connected to the cam, and the other end is abutted to the gas. The intermediate support point of the door rocker arm 7, the thin end of the intake sealing valve 3 and the exhaust sealing valve 4 are respectively connected to the two ends of the valve rocker arm, and the valve springs 6 are respectively disposed at the two ends of the cylinder head and the valve rocker arm, respectively It is used to maintain the closed state of the intake sealing valve 3 and the exhaust sealing valve 4. For the engine piston cylinder valve system shown in Figure 1, the working process includes:

Suction stroke: The piston 2 moves downward, the valve rocker arm 7 of the intake seal valve 3 is lowered, the intake seal valve 3 is opened, and the oil and gas mixture enters the piston space;

Compression stroke: The intake sealing valve 3 is closed, and the piston 2 moves upward to compress the oil and gas mixture entering the piston space;

Expansion power stroke: spark plug ignition, the oil and gas mixture in the piston space expands to do work, pushing the piston 2 downward;

Exhaust stroke: The piston 2 moves upward, one side of the exhaust sealing valve 4 of the valve rocker arm 7 descends, the exhaust sealing valve 4 opens, and the exhausted exhaust gas exits the piston space through the exhaust passage 11.

Referring to Figure 1, in the prior art suction/exhaust system, the intake sealing valve 3 is controlled by a spring-cam, and the cylinder takes in air by a vacuum negative pressure. When the gas in the intake passage is a normal pressure gas, the intake seal valve 3 can close the intake seal valve 3 by the force of the valve spring 6. However, when the gas in the intake passage is a pressurized gas, in order to close the open intake sealing valve 3, the force of the valve spring 6 must overcome the enormous pressure exerted by the pressurized gas on the intake sealing valve 3, otherwise it is easy to cause The intake sealing valve 3 is not tightly sealed. Summary of the invention

(1) Technical problems to be solved

In order to solve one or more of the problems described above, the present invention provides a balanced seal valve and a valve system using the balance seal valve to ensure a reliable seal of the seal valve even if the gas in the intake passage is a pressurized gas.

(ii) Technical solutions

According to one aspect of the invention, a balanced sealing valve is provided. The balance sealing valve comprises: a valve body and a valve core. Wherein: the middle portion of the valve body is hollowed out, forming a bottom-up first space and a second space in which the cylindrical axes coincide with each other; the radius of the first space is larger than the radius of the second space; An air inlet; the first air inlet is connected to the outside of the valve body through the first air inlet passage; and a conical disk opening is disposed at a lower portion of the first space. The spool includes a neck, a first piston, a connecting portion, a second piston, and a conical disc seal, wherein the axes are coincident; wherein, the neck is upward Passing through the second space; the first piston is located in the first space; the radius of the connecting portion is smaller than the radius of the first space; the upper surface area of the second piston exposed to the first space is not greater than the lower surface area of the first piston; The seal is matched to the conical disc opening. The spool is switched between an off state and a connected state. When the spool is in an off state, the upper surface of the first piston abuts against the upper surface of the first space, and the second piston and the first piston are both located in the first space. In close contact with the valve body portion located therearound, the lower surface of the first piston and the upper surface of the second piston are respectively located on the upper and lower sides of the first air inlet, and the conical disc seal is engaged with the cone at the lower portion of the first space a disc-shaped opening; when the spool is in a communicating state, the upper surface of the first piston is away from the upper surface of the first space and higher than the upper edge of the first intake port; the conical disc seal is disengaged from the conical disc-shaped opening The second piston is disengaged from the first space.

According to another aspect of the invention, a valve system is also provided. The valve system comprises: the balance sealing valve and the linkage mechanism described above. Wherein, the linkage mechanism is disposed between the main shaft and the balance sealing valve, and is used for controlling the timing of the balance sealing valve being in an off state or a connected state according to the phase information of the main shaft.

(3) Beneficial effects

It can be seen from the above technical solution that the balance sealing valve of the present invention and the valve system using the balanced sealing valve have the following beneficial effects:

(1) Due to the pressure balance of the pressure gas on the sealing valve spool, the force of the valve spring can overcome the huge pressure of the pressure gas on the valve core, and the sealing valve can be easily closed, so that the sealing valve is frequently high speed. In the opening and closing action, only a small force is required to be able to drive flexibly;

(2) The pressure applied to the valve core of the sealing valve is unbalanced, so that the valve core is always subjected to the axial thrust of the closing valve, and the valve spring with limited number of compressions and limited life can be omitted to improve the safety of the engine. And reliability;

(3) providing a third piston and a second intake port, and controlling opening and closing of the second intake port by the third piston, so that direct injection of one or more kinds of pressurized gas into the cylinder body can be controlled, so that The use of the balanced sealing valve of the present invention is more flexible and diverse. DRAWINGS

1 is a schematic cross-sectional view of a prior art engine piston cylinder valve system;

2 is a cross-sectional view showing a balanced sealing valve according to a first embodiment of the present invention; 3A is a cross-sectional view of a valve body in a balanced sealing valve according to a first embodiment of the present invention; FIG. 3B is a cross-sectional view of a valve core in a balanced sealing valve according to a first embodiment of the present invention; FIG. 4 is a balanced sealing valve according to a second embodiment of the present invention; Schematic diagram of the section;

Figure 5 is a cross-sectional view showing a spool of a balanced sealing valve according to a second embodiment of the present invention;

Figure 6A is a cross-sectional view showing the balance sealing valve in an OFF state according to a third embodiment of the present invention;

6B is a schematic cross-sectional view showing the balance sealing valve in a conducting state according to a third embodiment of the present invention;

Figure 7 is a cross-sectional view showing a spool of a balanced sealing valve according to a third embodiment of the present invention;

8A is a horizontal sectional view of the balance sealing valve of FIG. 6B along the second intake passage; FIG. 8B is a horizontal sectional view of the balance sealing valve along the second intake passage according to another embodiment of the present invention;

Figure 9 is a schematic view of a valve system according to an embodiment of the present invention;

Fig. 1 is a schematic view showing the cooperation relationship between the cam and the balance sealing valve in the linkage mechanism when the sealing valve in the valve system shown in Fig. 9 is in the conducting state;

Fig. 10B is a schematic view showing the cooperation relationship between the cam in the interlocking mechanism and the spool in the balance sealing valve when the sealing valve in the valve system shown in Fig. 9 is in the OFF state. detailed description

The present invention will be described in detail below with reference to the specific embodiments of the invention and the accompanying drawings. It should be noted that in the drawings or the description of the specification, the same reference numerals are used for similar or identical parts. Further, in the drawings, the shape or thickness of the embodiment can be expanded and simplified or conveniently indicated. Furthermore, elements or implementations not shown or described in the figures are known to those of ordinary skill in the art. In addition, although an example of a parameter containing a particular value may be provided herein, it should be understood that the parameter need not be exactly equal to the corresponding value, but rather may approximate the corresponding value within acceptable tolerances or design constraints.

For the sake of easy understanding, the main components involved in the present invention are first numbered as follows, as follows: [Main component symbol description]

1-cylinder block; 2-piston;

3-inlet sealing valve; 4-exhaust sealing valve;

5-cylinder head; 6-valve spring; Yan 8 - tappet;

9-cam; 10-injector;

11-exhaust passage; 12-intake passage;

001-spindle; 100-cylinder plate;

400-elastic reset member; 500-connector;

200-valve body;

210-first space; space;

230-first intake passage; 240-through hole;

250-positioning anti-friction component; 260-the first intake

270-valve;

300-valve;

310-neck; 320-j

330-connection;

350-cone disc seal; 360-600- linkage mechanism;

610- timing gear; 620-same chain;

630-same gear; 640-camshaft bearing housing;

650-camshaft; 660-cam;

670-pressure wheel; 700-cylinder interior.

2 is a schematic cross-sectional view showing a balanced sealing valve according to a first embodiment of the present invention. As shown in Fig. 2, the balanced seal valve of this embodiment includes: a valve body 200 and a valve body 300.

3A is a schematic cross-sectional view showing a valve body in a balance sealing valve according to a first embodiment of the present invention. Referring to Figures 2 and 3A, the valve body 200 is fixed to the cylinder plate 100, and the hollow portion thereof is hollowed out to form a cylindrical first-cone space 210 and a second space 220 whose axes coincide with each other. The radius of the first space 210 is greater than the radius of the second space 220, and a first air inlet is disposed on a side of the first space, and the first air inlet is connected to the outside of the valve body through the first air inlet passage 230; A lower portion of a space 210 is provided with a conical disk opening.

3B is a schematic cross-sectional view showing a spool in a balanced seal valve according to a first embodiment of the present invention. Referring to FIG. 2 and FIG. 3B, the valve core 300 includes a neck portion 310, a first piston 320, a connecting portion 330, a second piston 340 and a conical disk seal 350 whose axes coincide with each other; the neck portion 310 passes upward through the valve body. The second space 220 of the second space 220 extends; the first piston 320 is located in the first space 210, and is always in close contact with the side surface of the first space 210; the radius of the connecting portion 330 is smaller than the radius of the first space 210; the second piston 340 is exposed The upper surface area S2 of the first space 210 is equal to the lower surface area S1 of the first piston 320; the conical disc seal 350 matches the conical disc opening of the lower portion of the first space. The spool 300 is switched between an off state and a connected state.

Referring to FIG. 2, FIG. 3A and FIG. 3B, when the valve core 300 is in the OFF state, the upper surface of the first piston 320 abuts against the upper surface of the first space 210, and the second piston 340 and the first piston 320 are located at the a space 210 is in close contact with the valve body portion located therearound; the lower surface of the first piston 320 and the upper surface of the second piston 340 are respectively located on the upper and lower sides of the first air inlet, and the conical disc seal 350 is buckled A conical disk opening is formed in the lower portion of the first space 210 such that the first intake passage 230 is isolated from the cylinder interior 700.

Referring to FIG. 2, FIG. 3A and FIG. 3B, when the spool 300 is in the communicating state, the upper surface of the first piston 320 is away from the upper surface of the first space 210, and is still in close contact with the valve body portion located therearound, and is high. At the upper edge of the first air inlet; the second piston 340 is disengaged from the first space 210, and the conical disc seal 350 is disengaged from the conical disc opening. The first intake passage 230 communicates with the first space 210 through the periphery of the connecting portion 330, and the high pressure gas enters the cylinder interior 700 through the gap between the valve body 200 and the second piston 340.

For the balanced sealing valve of the present embodiment, when the first intake passage enters the high pressure gas, according to the Pascal principle, the lower surface of the first piston 320 and the upper surface of the second piston 340 are subjected to the same pressure due to the lower portion of the first piston 320. The area S1 of the surface is equal to the area S2 of the upper surface of the second piston 340 such that when the first piston 320 and the second piston 340 are in close contact with the valve body portion located therearound, respectively, the lower surface of the first piston 320 acts. The upward force F1 is equal to the downward pressure F2 acting on the upper surface of the first piston, specifically: when S1=S2, the pressure acting on the first piston 320 and the second piston 340 is balanced, that is, F1=F2, pressure The gas hardly generates axial thrust to the entire spool 300. Due to the pressure balance of the pressurized gas applied to the spool 300, the balance valve can be easily closed by simply relying on the force of the valve spring against the downward pressure of the pressurized gas applied to the second piston 340 of the balancing seal valve.

Theoretically, when the spool 300 is in the communication state, as long as the upper surface of the first piston 320 is higher than the upper edge of the first intake port, and it is ensured that the gas entering by the first intake port does not enter the second space 220. , the balance sealing valve can work normally. However, only the section of the fluid opening The largest product can ensure the smooth flow of the first air inlet, so that as much gas as possible can enter the first space for a limited time. Taking the engine as an example, the gas entering from the first intake port is air, and as much air as possible enters the cylinder, the air-fuel ratio can be increased, and the working efficiency of the fuel can be improved. Therefore, in the present embodiment, even when the spool 300 is in the communication state, the lower surface of the first piston 320 is higher than the upper edge of the first intake port, thereby ensuring the gas flow path entered by the first intake port. Completely unblocked.

As shown in FIG. 2, the first intake passage 230 extends obliquely downward along the periphery of the valve body to the first space 210, but the first intake passage 230 may also extend horizontally from the left or right side of the valve body to the first A space 210 can also be other settings. Regardless of which of the above, the method of the present invention can ensure a reliable sealing of the sealing valve, and should also be within the protection range of the present invention.

As shown in FIG. 2 and FIG. 3A, in order to maintain the stability of the valve core 300 in the off state and the connected state, the balance sealing valve of the embodiment further includes: a connecting base 500 connected to the neck 310 of the valve core 300, and the valve body The upper surface of the 200 is separated by a predetermined distance; the elastic returning member 400 is located between the connecting base 500 and the valve body 300, and the upper end thereof abuts against the lower surface of the connecting base 500, and the lower end thereof abuts against the upper surface of the valve body 200. It is used to maintain the cut-off state of the spool 300 with its elasticity. The elastic reset member 400 can be a spring or an elastic rubber. At this time, when the connecting seat 500 is subjected to the downward force, the elastic returning member 400 is compressed, the spool 300 is moved downward, the second piston 340 is disengaged from the first space 210, and the conical disc-shaped sealing member 350 is disengaged from the first space 210. The conical disc opening. The first intake passage 230 communicates with the cylinder interior 700. When the force is removed, the resilient return member 400 returns to its shape, the spool 300 moves upward, the second piston 340 enters the first space, and the conical disc seal 350 is closedly sealed with the conical disc opening of the first space 210. During this movement, the first piston 320 is always in close contact with the side wall of the first space 210.

As shown in FIG. 2, in order to maintain the directionality and stability of the neck 310 of the spool 300 in the second space 220, the valve body 200 further includes: a positioning anti-friction component 250, fixed in the second space, and sleeved Around the neck of the valve plug. The positioning wear reducing member 250 is a sliding sleeve or a linear motion ball bushing.

As shown in FIG. 3A and FIG. 4, in order to reduce the air resistance of the first piston 320 moving up and down in the first space, the portion of the first space located at the upper portion of the first piston communicates with the outside atmospheric pressure, and the periphery of the second space 220 The valve body portion is opened for the air in and out of the upper portion of the first piston 320. Vent hole 240. Preferably, the vents 240 are symmetrical.

Further, in order to allow the second piston 340 to smoothly enter the first space, a chamfer is provided at the upper edge of the second piston 340.

Up to this point, the balance sealing valve of the first embodiment of the present invention has been introduced. In this embodiment, the upper surface area S2 of the second piston 340 exposed to the first space 210 is equal to the lower surface area Sl of the first piston 320. A second embodiment in which the second piston 340 is exposed to the upper surface area S2 of the first space 210 is smaller than the lower surface area S1 of the first piston 320 will be given below.

4 is a cross-sectional view showing a balance sealing valve according to a second embodiment of the present invention. The balance seal valve of this embodiment is generally similar to the balance seal valve of Fig. 2 except that the valve body 300 further includes a valve seat 270. The valve seat 270 has a cylindrical shape, and at least a portion thereof is sleeved on a lower portion of the inner side of the first space 210, and is sealingly and fixedly connected with a valve body portion at a periphery thereof, and has an inner radius smaller than a radius of the first space, and a cylinder is formed at an upper portion thereof. The shaped cylinder has a lower portion forming the above-mentioned conical disc-shaped opening, and a top end surface of the valve seat 270 is lower than a lower edge of the first intake port.

Corresponding to the valve seat 270, the radius of the second piston 340 of the spool 300 is the same as the radius of the cylindrical cylinder of the valve seat, and the conical disc seal and the conical disc opening on the valve seat 270 are matched to each other, as shown in FIG. When the spool is in the off state, the second piston 340 is located in the cylindrical cylinder in close contact with the outer side of the cylindrical cylinder; when the spool is in the communication state, the second piston 340 is disengaged from the cylindrical cylinder. Since the inner radius of the valve seat 270 is smaller than the radius of the first space, the radius of the second piston 340 is the same as the radius of the cylindrical cylinder of the valve seat, and the radius of the first piston 320 is the same as the radius of the first space, therefore, the first piston The lower surface area S1 of 320 is greater than the upper surface area S2 of the second piston 340.

For the balanced sealing valve of the present embodiment, when the first intake passage enters the high pressure gas, according to the Pascal principle, the lower surface of the first piston 320 and the upper surface of the second piston 340 are subjected to the same pressure due to the lower portion of the first piston 320. The area S1 of the surface is larger than the area S2 of the upper surface of the second piston 340 so that the first piston 320 and the second piston 340 act on the lower surface of the first piston 320 when they are in close contact with the valve body portion located therearound, respectively. The upward force F1 is greater than the downward pressure F2 acting on the upper surface of the first piston, specifically: when S1 S2, the axial thrust of the pressurized gas to the entire spool 300 is upward, that is, F1 F2, which is equivalent to the balanced sealing valve. The spool 300 is always subjected to the thrust of the closing valve, in which case the conical disc seal 350 can be tightly engaged in the conical disc opening of the first space 210 even without the valve spring. therefore, In this embodiment, the valve spring having a limited number of compression times can be omitted, which means that the safety and reliability of the engine are improved.

Theoretically, as long as the top end face of the valve seat 270 is lower than the upper edge of the first intake port, the gas entering from the first intake port can enter the first space of the lower surface of the first piston. Also, based on the largest fracture area of the fluid opening, in the present embodiment, the top end face of the valve seat 270 of the balance sealing valve needs to be lower than the lower edge of the first intake port, thereby maximizing the sectional area of the fluid opening. However, the present invention is not limited thereto, and as long as the top end surface of the valve seat 270 is lower than the upper edge of the first intake port, it should be included in the protection scope of the present invention.

In this embodiment, the valve seat 270 can be made of a copper material, and the conical disc-shaped opening and the conical disc-shaped seal 350 of the valve core are ground and sealed. The outer radius of the valve seat 270 is larger than the radius of the first space 210. In this case, it is necessary to provide a larger cylindrical space at the periphery of the first space to accommodate the valve seat 270 to seal the valve seat 270. The lower portion of the inner side of the first space 210. In another preferred embodiment of the invention, the outer radius of the valve seat 270 can also be equal to the radius of the first space.

Up to this point, the balance sealing valve of the second embodiment of the present invention has been completed. In this embodiment, the upper surface area S2 of the second piston 340 exposed to the first space 210 is greater than the lower surface area S1 of the first piston 320.

The balanced sealing valve of the above two embodiments is suitable for controlling the pressure gas entering the cylinder, such as an aerodynamic engine, an internal combustion engine, etc., which can control the entry and closing of the pressurized gas very conveniently, avoiding the prior art The pressure of the pressure gas on the sealing valve causes the sealing valve to be tightly sealed.

6A and 6B are schematic cross-sectional views showing a balanced seal valve according to a third embodiment of the present invention, wherein: the spool is in an open state in Fig. 6A; and the spool is in a connected state in Fig. 6B. As shown in FIG. 6A and FIG. 6B, in the embodiment, the valve body 200 further includes: a second air inlet located on a side of the first space 210, the second air inlet being connected to the valve through the second air inlet passage 260 Outside the body, the projections of the second intake passage 260 and the first intake passage 230 on the horizontal plane are offset from each other by a predetermined angle θ.

Figure 7 is a cross-sectional view showing a spool of a balanced seal valve in accordance with a third embodiment of the present invention. As shown in Fig. 7, the spool 300 further includes: a third piston 360 located between the first piston 320 and the second piston 340 in a cylindrical shape, and the thickness of the cylindrical portion is greater than the longitudinal length of the second intake port.

When the spool 300 is in the off state, the third piston 360 is equal to the second intake port, and the outside The cylindrical surface seals the second air inlet as shown in FIG. 6A; when the valve core is in the communicating state, the valve core moves downward, and the lower surface of the first piston 320 and the upper surface of the third piston 360 are respectively located in the second inlet. Upper and lower sides of the port, and the upper surface of the third piston 360 is lower than the upper edge of the first intake port.

When the balance sealing valve of the present embodiment is switched from the off state to the communication state, the gas entering the second intake passage is connected by the first piston 320 and the third piston 360 as the second piston 340 is disengaged from the first space. The gap around the portion 330 enters, mixes with the gas entering the first intake passage, and enters the interior of the cylinder through the gap between the valve body and the first piston, as shown in Fig. 6B.

In order to make full use of the stroke of the valve, the upper edge of the second intake port is equal to the upper edge of the first intake port. Of course, it can also be slightly lower than the upper edge of the first air inlet.

In the practical application of the balance sealing valve of this embodiment, it is necessary to prevent the danger caused by the pressure difference between the gas entering the first intake passage and the second intake passage entering the gas. Taking the compressed air from the first intake passage and the natural gas from the second intake passage as an example, the natural gas entering the second intake passage needs to be decompressed, but the pressure of the decompressed natural gas should be greater than Compress the pressure of the gas to prevent the compressed gas from entering the gas cylinder pressure relief valve.

Further, the second intake passage 260 and the first intake passage 230 are offset from each other by a predetermined angle θ. For ease of understanding, the first inlet and the second inlet are described as shown in Fig. 8A and Fig. 8B. Figure 8 is a horizontal sectional view of the balance sealing valve shown in Figure 6A along the second intake passage. In the present embodiment, θ = 180°. At this time, the pressure of the natural gas is higher than the pressure of the compressed air. The natural gas can directly enter the compressed air inlet, where it mixes with the air, and the mixed gas enters the inside of the cylinder through the gap between the valve body and the spool. Figure 8 is a horizontal cross-sectional view of the balanced seal valve along the second intake passage in accordance with another embodiment of the present invention. In this case, θ = 90 °. In the Venturi effect zone, high-pressure natural gas draws compressed air into the rotating mixture before entering the compressed air intake main passage, where it is mixed with air. In this case, the mixing of natural gas and compressed air will be more uniform.

In a further embodiment of the present invention, the balance sealing valve may further include: a plurality of the second air inlets, and a plurality of third pistons respectively corresponding to the plurality of second air inlets to control the three paths Or more of the other gases entering the cylinder.

Up to this point, the balance sealing valve of the third embodiment of the present invention has been completed. The balanced sealing valve of the present embodiment is suitable for the occasion of controlling two or more pressurized gases entering the cylinder, such as a natural gas engine. At this time, the first intake passage enters the pressurized gas and the second intake passage enters. Pressure Natural gas, which can easily control the entry and closing of pressurized gas and natural gas at the same time. It is emphasized again that the pressure at which the second intake passage enters the compressed natural gas should be slightly higher than the pressure of the pressurized gas.

Various embodiments of the balanced seal valve have been given above. In practical applications, the state of the seal valve is closely related to the timing of entry of the pressurized gas. Taking the engine in the background art as an example, the sealing valve needs to be opened only when it is in the intake stroke, and the sealing valve needs to be closed when the other is in the fuel injection, ignition, and expansion strokes. This inevitably involves an interlocking mechanism for controlling the opening and closing timing of the sealing valve in accordance with the state of motion of the main shaft, which is an indispensable device for the practical application of the balanced sealing valve of the present invention.

According to another aspect of the present invention, there is also provided a valve system to which the above balanced seal valve is applied. The valve system includes: a balance sealing valve and a linkage mechanism. The linkage mechanism is disposed between the main shaft and the balance sealing valve, and is configured to control the timing of the spool of the balance sealing valve in an off state and a connected state according to the phase information of the main shaft.

In a fourth embodiment of the present invention, the linkage mechanism includes: a position sensor for acquiring phase information of the spindle; an external electrical expansion mechanism located outside the cylinder block, the top end of which is connected to the neck of the balance sealing valve , used to expand and contract according to the phase information of the main shaft to control the timing of the valve core of the balance sealing valve in the off state and the connected state.

In a fifth embodiment of the invention, a linkage mechanism 600 of purely mechanical construction is also provided. Referring to FIG. 9, the linkage mechanism 600 includes: a cam shaft 650 disposed on the outer periphery of the cylinder through the camshaft bearing housing 640, the direction of the axis being parallel to the axial direction of the main shaft; the same gear 630 disposed on the camshaft 650 The outer end is connected to the timing gear 610 sleeved on the main shaft by the same chain 620; the pressure wheel 670 is located on the connecting base 500, the connecting seat 500 is fixedly connected to the neck 310 of the balance sealing valve; the cam 660, the setting On the camshaft 650, the outer side of the cam 660 abuts against the pressure wheel 670.

In the linkage mechanism 600, the timing gear 610 on the main shaft 001 transmits the phase information of the main shaft to the cam 660 through the homogenous gear 630 through the same chain 620, and the cam 660 controls the axial movement of the valve core of the balance sealing valve through the pressure wheel 670. , to achieve the action of opening or closing the balance sealing valve. When the machine is running to the intake stroke, the protrusion of the cam 660 presses down the spool of the balance sealing valve through the pressure wheel 670, the second piston 340 of the spool opens, and the pressurized gas enters the cylinder interior 700 through the first intake passage. As shown in Figure 10A. When the intake stroke is over, under the action of the compression spring, The spool moves upward, and the second piston 340 of the spool is closed, so that the pressurized gas continues to expand in the cylinder 700 to perform work, which can reduce the residual pressure and save energy, as shown in FIG. 10B.

Thus far, the valve system of the balance sealing valve of the fourth embodiment and the fifth embodiment of the present invention has been described.

It should be noted that the above definitions of the various elements are not limited to the specific structures or shapes mentioned in the embodiments, and those skilled in the art can simply and well replace them, for example:

(1) The shape of the sealing surface of the conical disc seal member 350 of the present invention may be a conical shape, a dish shape or a platform shape, and the corresponding sealing surface of the conical disc-shaped opening of the valve body is a surface matched thereto;

(2) The conical disc seal member 350 and the second piston 340 may be integrally formed or may be separately manufactured and joined together by conventional methods such as splicing, riveting or screwing. The separately manufactured conical disc seal 350 and the second piston 340 will be advantageous for assembly of a valve seat in a balanced seal valve having a valve seat as in the second embodiment;

(3) The conical disc seal 350 and the second piston 340 may be made of the same material or may be made of different materials;

(4) The compression spring 400 may be replaced by a tension spring, and the direction of the force acting on the neck of the valve core is the same as that of the first embodiment, and those skilled in the art should know the arrangement of the tension spring, which will not be described in detail herein.

In summary, the present invention discloses a balanced sealing valve and a valve system including the same. The balance sealing valve is provided with pistons on the upper and lower sides of the intake port, and the Pascal's principle is used to offset the pressures of the two pistons, so that when the gas in the intake passage is pressurized gas, the seal can be reliably sealed. The valve is closed, and in frequent high-speed opening and closing operations, only a small amount of force is required to drive flexibly. The specific embodiments of the present invention have been described in detail with reference to the preferred embodiments of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims

Rights request

1. A balanced seal valve, characterized in that it includes: a valve body and a valve core, wherein: the middle part of the valve body is hollowed out to form a bottom-up first space and a second cylindrical space whose axes overlap with each other. space; the radius of the first space is greater than the radius of the second space; a first air inlet is provided on the side of the first space; the first air inlet is connected to the outside of the valve body through a first air inlet channel ; Set a conical disk-shaped opening in the lower part of the first space;

The valve core includes a neck with overlapping axes, a first piston, a connecting part, a second piston and a cone-shaped seal; wherein, the neck passes upward through the second space; the first piston is located In the first space; the radius of the connecting portion is smaller than the radius of the first space; the upper surface area of the second piston exposed to the first space is not larger than the lower surface area of the first piston; The conical disc-shaped seal matches the conical disc-shaped opening;

The valve core switches between a cut-off state and a connected state. When the valve core is in the cut-off state, the upper surface of the first piston abuts the upper surface of the first space, and the second piston and The first pistons are located in the first space and are in close contact with the valve body portion located around them. The lower surface of the first piston and the upper surface of the second piston are respectively located in the first air inlet. On the upper and lower sides of the opening, the conical disk-shaped sealing member is fastened to the conical disk-shaped opening in the lower part of the first space; when the valve core is in a connected state, the upper surface of the first piston is away from the third The upper surface of a space, and is higher than the upper edge of the first air inlet; the conical disc-shaped seal is detached from the conical disc-shaped opening, and the second piston is detached from the first space .

2. The balanced seal valve according to claim 1, characterized in that: when the valve core is in a connected state, the lower surface of the first piston is higher than the upper edge of the first air inlet.

3. The balanced seal valve according to claim 1, characterized in that:

The valve body also includes: a valve seat, which is cylindrical, at least part of which is sleeved on the lower part inside the first space, the top end surface of the valve seat is lower than the upper edge of the first air inlet, and is located Its peripheral valve body part is sealed and fixedly connected; the inner radius of the valve seat is smaller than the radius of the first space, its upper part forms a cylindrical cylinder, and its lower part forms the conical disk-shaped opening;

When the valve core is in the cut-off state, the second piston is located in the valve seat cylindrical cylinder and is in close contact with the outer surface of the cylindrical cylinder; when the valve core is in the connected state, the second piston is in the connected state. The two pistons are detached from the cylindrical cylinder.

4. The balanced seal valve according to claim 3, characterized in that: the top of the valve seat The bottom end surface is lower than the lower edge of the first air inlet.

5. The balanced seal valve according to claim 3, characterized in that: the outer radius of the valve seat is larger than the radius of the first space.

6. The balanced seal valve according to claim 1, characterized in that:

The valve body also includes: a second air inlet, located on the side of the first space, connected to the outside of the valve body through a second air inlet channel, the second air inlet channel being in contact with the first air inlet channel. The projections on the horizontal plane are staggered by a preset angle Θ;

The valve core also includes: a third piston, located between the first piston and the second piston, having a cylindrical shape, and the thickness of the cylindrical shape is greater than the longitudinal length of the second air inlet;

When the valve core is in the cut-off state, the third piston is at the same height as the second air inlet, and its outer cylindrical surface seals the second air inlet; when the valve core is in the connected state, the first The lower surface of the piston and the upper surface of the third piston are respectively located on the upper and lower sides of the second air inlet, and the upper surface of the third piston is lower than the upper edge of the first air inlet.

7. The balanced seal valve according to claim 6, characterized in that: the θ=90° or 180. .

8. The balanced seal valve according to claim 6, characterized in that: the upper edge of the second air inlet is at the same height as the upper edge of the first air inlet.

9. The balanced seal valve according to claim 6, characterized in that it includes a plurality of second air inlets; each of the second air inlets has a corresponding third piston matching it, and the plurality of second air inlets are matched with each other. The second air inlets are staggered from each other in the height direction.

10. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the first air inlet passage is a horizontal air inlet passage or an air inlet passage inclined downward.

11. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the upper edge of the second piston is provided with a chamfer.

12. The balanced seal valve according to any one of claims 1 to 9, further comprising:

The connecting seat is connected to the neck of the valve core and is separated from the upper surface of the valve body by a preset distance. The elastic return member is located between the connecting seat and the valve body, and its upper end is in contact with the valve body. The lower surface of the connecting seat has its lower end in contact with the upper surface of the valve body to utilize its elasticity to maintain the valve. The cut-off state of the core.

13. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the valve body further includes:

The positioning anti-friction component is fixed in the second space and sleeved around the neck of the valve core.

14. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the valve body further includes:

A plurality of ventilation holes are provided on the valve body around the first space to connect the portion of the first space located on the upper part of the first piston to the outside atmospheric pressure.

15. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the shape of the sealing surface of the conical disk-shaped seal is conical, dish-shaped or platform-shaped, and the conical disk-shaped opening The corresponding sealing surface is the matching surface.

16. The balanced seal valve according to any one of claims 1 to 9, characterized in that: the conical disk-shaped seal and the second piston are integrally formed or fixedly connected by welding, riveting or screwing. .

17. A valve system including the balanced seal valve according to any one of claims 1 to 16, characterized in that it also includes:

A linkage mechanism is provided between the main shaft and the balanced sealing valve, and is used to control the timing when the valve core of the balanced sealing valve is in a cut-off state or a connected state based on the phase information of the main shaft.

18. The valve system according to claim 17, characterized in that: the linkage mechanism includes:

Position sensor to obtain phase information of the spindle; and

The external electric telescopic mechanism is located outside the cylinder, and its top end is connected to the neck of the balanced seal valve. It is used to expand and contract according to the spindle phase information obtained by the position sensor to control the valve core of the balanced seal valve to be in the position of Timing of cut-off state and connected state.

19. The valve system according to claim 17, characterized in that: the linkage mechanism includes:

The camshaft is arranged on the periphery of the cylinder through the camshaft bearing seat, and the direction of its axis is parallel to the direction of the axis of the main shaft;

A synchronization gear is provided at the outer end of the camshaft, and is connected to the timing gear sleeved on the main shaft through a synchronization chain; The pressure wheel is located at the connection seat fixedly connected to the neck of the valve core of the balanced seal valve; and the cam is provided on the camshaft, and its outer surface is in contact with the pressure wheel; in the linkage mechanism, the main shaft The timing gear transmits the phase information of the main shaft to the cam through the synchronization chain and the synchronization gear. The cam controls the axial movement of the valve core of the balance seal valve through the pressure wheel to open or close the balance seal valve.