CN214304271U - High-pressure gas tank pump - Google Patents
High-pressure gas tank pump Download PDFInfo
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- CN214304271U CN214304271U CN202120368642.2U CN202120368642U CN214304271U CN 214304271 U CN214304271 U CN 214304271U CN 202120368642 U CN202120368642 U CN 202120368642U CN 214304271 U CN214304271 U CN 214304271U
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Abstract
The utility model provides a high-pressure gas tank pump, including the low pressure intake pipe, the high-pressure blast pipe, the pressure cylinder and the transfer line of the piston of connecting in the pressure cylinder, the volume in the chamber that holds of a plurality of pressure cylinders diminishes along the gas flow direction in proper order, be equipped with one-way water conservancy diversion spare on air inlet and/or the gas outlet, one-way water conservancy diversion spare has a plurality of bottoms and meets in proper order to enclose and synthesizes annular valve, be the open mode when a plurality of valve phase separations, be the closed mode when a plurality of valve phase accumulations, this one-way water conservancy diversion spare is in under the state that is parallel with the gas flow direction after opening completely, make this one-way water conservancy diversion spare have very low resistance coefficient after opening completely, so that this high-pressure gas tank pump has the application prospect of superhigh pressure, the pressure cylinder that the grade is the same carries on the back to set up, and receive the corresponding pole control on the both ends pole section of transfer line respectively, the high-pressure gas tank pump can achieve the aim of pumping high-pressure gas in a multistage synchronous and continuous mode.
Description
Technical Field
The utility model relates to a high compression pump mechanical equipment field, concretely relates to high-pressure gas tank pump.
Background
The high-pressure air pump is a pump for pressurizing air to output high-pressure air, and is a common air pump. In order to achieve the purpose of outputting high pressure, the requirement of the high-pressure air pump on the tightness and the non-return property of the air flow is high, therefore, the essential component of the high-pressure air pump is a check valve, and at present, the check valve applied to the high-pressure air pump adopts a lifting check valve in structure, for example, the Chinese patent application No. CN201520244765.X discloses a novel high-pressure air pump air inlet one-way valve, the air inlet one-way valve of the high-pressure air pump mainly comprises a valve body and a valve core, wherein the valve body is provided with an air inlet and an air passage which are communicated, the valve core comprises a valve rod, a sealing gasket, a return spring and a fixing piece, the valve rod penetrates through the air passage, the top end of the valve rod is connected with one end of a return spring through a fixing piece, the other end of the return spring is fixed in the air inlet hole, the bottom end of the valve rod is fixedly connected with the sealing gasket, and the sealing gasket is a high-temperature-resistant polytetrafluoroethylene sealing gasket.
Although the check purpose can be realized by the high-pressure air inlet check valve, the valve rod on the valve core of the high-pressure air inlet check valve is directly arranged in the air passage through which high-pressure gas flows, and when the valve core is in an open state, the check piece, namely the sealing gasket, on the valve rod is still arranged in a mode of being perpendicular to the air passage, so that the high-pressure gas can be greatly resisted in the air passage, the flow of the high-pressure gas is influenced, the resistance coefficient of the check valve is too large, and the energy conversion rate of the high-pressure air pump using the check valve is lowered.
It should be noted that, in the prior art, the number of stages of most high-pressure air pumps is basically defined by the number of the pressure cylinders, and the volumes of the pressure cylinders do not decrease sequentially, and for such air pumps which are set purely by the number of the pressure cylinders, although the amount of the output gas increases, the final output gas pressure value does not increase.
Although there are high pressure air pumps with the number of stages adapted to the volume of the pressure cylinder, that is, the higher the number of stages, the smaller the volume of the pressure cylinder, for example, a high pressure air pump disclosed in chinese patent application No. CN201110364595.5, in which the volumes of the pressure cylinders sequentially set in the flowing direction of the air are sequentially reduced, so that it can achieve the purpose of further compressing the air, the pressure cylinders of different stages in the above-mentioned high pressure air pump of the prior art are basically nested in sequence in structure, the number of stages of the pressure cylinders is still limited, so that the pressure value of the final output air of the air pump is not very high, and the pressure is intermittently increased step by step in structure, and the timeliness of the output air is not high.
SUMMERY OF THE UTILITY MODEL
To prior art not enough, the utility model provides a high-pressure gas tank pump to solve the following technical problem that exists among the prior art: the case of the check valve of current high pressure air pump is because of directly setting up in the air flue of high-pressure gas circulation to when under the open mode, the backstop on the case still is the form setting of perpendicular to air flue, and this will make high-pressure gas can receive very big resistance in the air flue, and the resistance coefficient of check valve is too big, influences high-pressure gas's circulation, also makes the energy conversion rate of using the high pressure air pump of this kind of check valve step down.
The technical scheme of the utility model is realized like this:
a high-pressure gas tank pump comprises a low-pressure gas inlet pipe, a high-pressure gas outlet pipe and a transmission rod capable of reciprocating along the axis of the high-pressure gas inlet pipe and the axis of the high-pressure gas outlet pipe, wherein a plurality of pressure cylinders are connected between the low-pressure gas inlet pipe and the high-pressure gas outlet pipe in series, the volumes of containing cavities of the plurality of pressure cylinders are sequentially reduced along the gas flowing direction, pistons are arranged in the pressure cylinders, the plurality of pistons are connected with the transmission rod, gas inlets and gas outlets are arranged in the plurality of pressure cylinders, and one-way flow guide pieces are arranged on the gas inlets and/or the gas outlets;
the one-way flow guide piece is provided with a plurality of valve valves of which the bottoms are sequentially connected to enclose and form a ring shape, an internal space formed by the enclosing of a plurality of valve flap films forms an airflow channel for the circulation of gas, the distance from the top to the bottom of the valve valves is larger than the radius of the airflow channel, the valve flap films are in an opening state when being separated, so that the gas can pass through, in the process of opening the valve valves, high-pressure gas can directly flow out from the space between the valve valves after the gas impacts the valve valves and the valve flap films are separated from each other, the directly flowing gas can not be blocked by the valve valves, the circulation efficiency of the gas is improved, and in the process of separating the valve valves from each other under the impact of the gas, the airflow channel can be enlarged, the blocking effect of the valve valves can be smaller and smaller, when the valve flap films are impacted to be parallel to the flowing direction of the gas in the airflow channel, the valve clack membrane is completely opened, because the valve clack membrane is in a state parallel to the gas flow direction at the moment, the resistance coefficient of the valve clack membrane to gas is the lowest at the moment, and compared with the check piece of the traditional lifting one-way valve in a state that the check piece is still vertical to the gas flow direction in an opening state, undoubtedly, the resistance coefficient of the one-way flow guide assembly in the opening state is greatly lower than that of the traditional lifting one-way valve in the opening state, therefore, the one-way flow guide piece has a very low resistance coefficient in the opening state, and further the high-pressure gas tank pump can be ensured to have a high energy conversion rate. When gas flows from the top to the bottom of the valve, the gas drives the valve to rotate towards the center of the airflow channel, so that the valve rotates towards the center of the airflow channel 9 and is mutually polymerized, thereby playing a role of blocking the airflow channel, therefore, the valve is in a closed state when being mutually polymerized, the purpose of reverse check is realized, the valve is in a closed state when being mutually polymerized, so as to block the gas from passing through, when the valve is mutually polymerized, the side edge of any valve is tightly abutted with the side edge of the valve adjacent to the valve, because the distance from the top to the bottom of the valve is greater than the radius of the airflow channel, in the process of closing and rotating, the valve flap film can be abutted with other valve without rotating to the state parallel to the cross section of the airflow channel to form a closed surface, the rotation amplitude of the valve is reduced, so that the purpose of reducing the back stepping amount during closing is achieved, and meanwhile, the valve in the closed state is not perpendicular to the airflow channel, so that the opening speed of the valve is increased in the opening process, and the opening response speed of the one-way flow guide piece is increased.
Furthermore, a plurality of the pressure cylinder hold the chamber and all be cylindricly, and a plurality of the pressure cylinder be cylindric the central line that holds the chamber and be parallel arrangement, be favorable to the transfer line to be connected with the piston in the pressure cylinder.
Furthermore, the central axis of the transmission rod is parallel to the central line of the containing cavity of the pressure cylinder, the transmission rod is provided with a plurality of push-pull rods parallel to the transmission rod, and the end parts of the push-pull rods are connected with the piston.
Further, the ratio of the radii between the receiving cavities of any two adjacent pressure cylinders in the gas flow direction is equal.
Further, the ratio of the radius between the containing cavities of any two adjacent pressure cylinders in the gas flow direction is 1.5-2.5.
Further, the number of the pressure cylinders is set to be 2 to 12.
Further comprises a driving motor and an eccentric disc, one end of the transmission rod is provided with a central chute which is vertical to the central axis of the transmission rod, the output shaft of the driving motor is connected with the eccentric disc, the eccentric disc is provided with an eccentric deflector rod, the eccentric deflector rod is arranged in the central chute in a sliding way, the eccentric deflector rod is arranged on the eccentric disc in an eccentric way with the output shaft of the driving motor, because the central sliding groove is vertical to the central axis of the transmission rod and the eccentric deflector rod slides in the central sliding groove, the central sliding groove can eliminate the influence of the pushing force of the eccentric deflector rod in the direction perpendicular to the axis of the transmission rod, thereby realizing the purpose of converting the rotation motion of the eccentric deflector rod into the reciprocating linear motion of the transmission rod, therefore, the eccentric disc driven by the driving motor achieves the purpose of driving the transmission rod to reciprocate.
Furthermore, the hydraulic cylinder device further comprises a rigid shell, wherein the pressure cylinders are arranged in the rigid shell, a sliding groove penetrating through the rigid shell is formed in the middle of the rigid shell, and the transmission rod is arranged in the sliding groove in a sliding mode.
Furthermore, the transmission rod penetrates through the rigid shell through the sliding groove, the push-pull rods parallel to the transmission rod are arranged on the rod sections at the two ends of the transmission rod after penetrating out of the rigid shell, the nth pressure cylinder in the gas flow direction is an n-level pressure cylinder, the number of the n-level pressure cylinders is at least two, and n is larger than or equal to 1.
Furthermore, two n-stage pressure cylinders with the same stage number are arranged on the rigid shell in a back-to-back manner, so that all the pressure cylinders with the same stage number are in opposite action states, and only two action states, namely exhaust action states and suction action states, exist in the normal operation process of the pressure cylinders, therefore, the pressure cylinders with the same stage number are arranged on the back and are respectively controlled by the push-pull rods on the rod sections at the two ends of the transmission rod, so that the high-pressure gas tank pump can achieve the purpose of continuously pumping high-pressure gas, and can also play a role in balancing the stress of each point of the transmission rod.
Furthermore, the projection of the valve on the longitudinal section of the airflow channel is in the shape of an isosceles triangle, and when a plurality of valve valves are polymerized, the valve valves are in the shape of a cone or a pyramid, wherein the longitudinal section of the gas flow channel is the section of the flow channel parallel to the flow direction of the gas, the cross section of the gas flow channel is the section of the gas flow channel perpendicular to the flow direction of the fluid medium, because the sealing surface formed by the close contact of the valve clack films is conical or pyramid-shaped in the closed state, the compression strength of the sealing surface in the axial direction of the gas flow channel is greatly improved, and when gas flows backwards, the greater the fluid pressure to which the conical or pyramidal sealing surface is subjected, the tighter the connection between the valve flap membranes, the sealing performance of the sealing surface is higher, and the high-pressure gas tank pump has the characteristic of high non-return sealing performance.
Furthermore, a plurality of valve valves are provided with reinforced steel plates with the shapes matched with those of the valve valves.
The valve comprises a plurality of valve valves, and is characterized by further comprising peripheral thin films sleeved on the outer sides of the valve valves, wherein the peripheral thin films are cylindrical or prismatic, and the bottoms of the peripheral thin films are connected with the bottoms of the valve valves.
Furthermore, a matched convex part matched with the inner cavity of the one-way flow guide part in a closed state is arranged at the position, corresponding to the air outlet, on the piston, when the pressure cylinder is in a state of extruding air, the matched convex part on the piston can enter a space surrounded by a valve on the air outlet so as to play a role in reducing the residual gas in the pressure cylinder, and the residual gas in the cylinder can be controlled within 0.5% by arranging the matched convex part.
Furthermore, a matched concave cavity matched with the shape of the one-way flow guide piece in a closed state is arranged at the position, corresponding to the air inlet, of the piston, when the piston performs extrusion exhaust in the pressure cylinder, the piston is close to the cylinder bottom of the pressure cylinder, and the valve clack film at the air inlet is positioned in the pressure cylinder, so that the matched concave cavity matched with the shape of the one-way flow guide piece in the closed state is arranged on the inner surface of the corresponding piston, and when the piston approaches the cylinder bottom of the pressure cylinder in the extrusion exhaust process, the one-way flow guide piece in the closed state enters the matched concave cavity, so that the purpose that the piston can be fully attached to the cylinder bottom of the pressure cylinder is achieved, and full exhaust is ensured.
The utility model has the advantages that: the valve valves are arranged on the air inlet and/or the air outlet and form an integral one-way flow guide part in a surrounding way, the aim of one-way opening or one-way non-return is realized by utilizing the phase separation or the phase polymerization of the valve valves, in the opening process, high-pressure air can directly flow through gaps among the valve valves, the directly flowing air cannot be blocked by the valve valves, so that the resistance coefficient is reduced, the air flowing efficiency is improved, and the valve valves can be in a state parallel to the air flowing direction after being completely opened, so that the one-way flow guide part has a very low resistance coefficient in a completely opened state, the high-pressure air box pump can have a high energy conversion rate, the high-pressure air box pump has an ultrahigh pressure application prospect, the valve valves have small rotating amplitude, and the function of effectively reducing the back-stepping amount of air can be realized, the valve in the closed state is not vertical to the airflow channel, so that the opening speed of the valve is increased in the opening process, and the opening response speed of the one-way flow guide piece is increased; the pressure cylinders with the same series are arranged in a back-to-back mode and are controlled by the corresponding push-pull rods on the rod sections at the two ends of the transmission rod respectively, so that the high-pressure gas tank pump can achieve the purpose of pumping high-pressure gas in a multistage synchronous and continuous mode, the matched concave cavity plays a role in ensuring that the piston can fully fit the cylinder bottom of the pressure cylinder in the exhaust process, sufficient exhaust is ensured, and the matched convex piece plays a role in reducing the residual quantity of gas in the pressure cylinder.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive exercise.
Fig. 1 is a schematic structural view of a high-pressure gas tank pump according to the present invention;
fig. 2 is a schematic view of the internal structure of a high-pressure gas tank pump according to the present invention;
FIG. 3 is an enlarged view of a portion A of FIG. 2;
FIG. 4 is a partial enlarged view of portion B of FIG. 2;
FIG. 5 is a view showing a connection relationship between the eccentric shift lever and the center slide groove;
FIG. 6 is a schematic diagram of the structure of the high-pressure gas tank pump of the present invention in two stages;
FIG. 7 is a schematic view of the rigid housing of FIG. 1 looking down;
FIG. 8 is a schematic structural view of the one-way flow guide assembly in an open state;
fig. 9 is a schematic structural view of the unidirectional flow guide assembly in a closed state.
The attached drawings are as follows: 1. a low-pressure air inlet pipe; 2. a high pressure exhaust pipe; 3. a transmission rod; 31. a push-pull rod; 32. a central chute; 4. a pressure cylinder; 4-1, a primary pressure cylinder; 4-2, a secondary pressure cylinder; 4-3, a three-stage pressure cylinder; 4-4, four-stage pressure cylinder; 5. a piston; 51. matching a convex part; 52. matching a concave cavity; 6. an air inlet; 7. an air outlet; 8. a valve; 81. the valve clack is connected with a ring; 9. an air flow channel; 10. a drive motor; 11. an eccentric disc; 12. an eccentric deflector rod; 13. a rigid housing; 14. a sliding groove; 15. a mechanism box; 16. reinforcing a steel plate; 17. a peripheral film; 18. a reduction gearbox.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Referring to fig. 1 to 9, a high pressure gas tank pump comprises a low pressure gas inlet pipe 1, a high pressure gas outlet pipe 2 and a transmission rod 3 capable of reciprocating along the axis of the low pressure gas inlet pipe 1 and the high pressure gas outlet pipe 2, wherein a plurality of pressure cylinders 4 are connected in series between the low pressure gas inlet pipe 1 and the high pressure gas outlet pipe 2, the volumes of the accommodating cavities of the plurality of pressure cylinders 4 are sequentially reduced along the gas flowing direction, pistons 5 are arranged in the pressure cylinders 4, the plurality of pistons 5 are connected with the transmission rod 3, under the reciprocating action of the transmission rod 3, the transmission rod 3 simultaneously drives the pistons 5 in the plurality of pressure cylinders 4 to reciprocate to play the roles of synchronously compressing and synchronously expanding the pressure cylinders, gas inlets 6 and gas outlets 7 are arranged in the plurality of pressure cylinders 4, referring to fig. 2 to 4, one-way guide members are arranged on the gas inlets 6 and/or the gas outlets 7, wherein the directions of the one-way guide members on the gas inlets 6 and the gas outlets 7 are the same, the one-way flow guide piece plays a role in preventing gas from flowing reversely;
referring to fig. 3,4, 8 and 9, the one-way guiding member has a plurality of valve flap membranes 8 whose bottoms are sequentially connected to enclose an annular shape, wherein the valve flaps 8 themselves can rotate relative to the bottoms, the bottoms of the valve flaps 8 enclose a valve flap connecting ring 81, the valve flap connecting ring 81 is used for installing and connecting the pressure cylinder 4, the inner space enclosed by the valve flaps 8 forms an airflow channel 9 for the circulation of gas, when the gas passes through the airflow channel 9 from the bottom of the valve flap membrane 8 to the top, the valve flaps 8 can be separated from each other under the impact of the gas, so that the valve flaps 8 can pass through the airflow channel 9 without obstruction, therefore, the valve flaps 8 are in an open state when separated, and the gas impacts the valve flaps 8 and separates the valve flaps 8 from each other when the valve flaps 8 are opened, the high pressure gas can directly flow out from the space between the valve valves 8, the directly flowing gas can not be blocked by the valve valves 8, the gas flow efficiency is improved, the blocking effect of the valve valves 8 is smaller and smaller because the gas flow channels 9 are continuously enlarged in the process that the valve valves 8 are separated from each other under the impact of the gas, when the valve valves 8 are impacted to be parallel to the flow direction of the gas in the gas flow channels 9, the valve valves 8 are completely opened, because the valve valves 8 are in the state of being parallel to the gas flow direction, the resistance coefficient of the valve clack film 8 to the gas is the lowest at the moment, compared with the state that the check member of the traditional lifting one-way valve is still in the state of being perpendicular to the gas flow direction under the opening state, the resistance coefficient of the one-way flow guiding component under the opening state is undoubtedly lower than that under the opening state of the traditional lifting one-way valve, the resistance coefficient of the one-way flow guide piece can be reduced to 0.5 or below, so that the one-way flow guide piece has a very low resistance coefficient in an opening state, and the function of ensuring that the high-pressure gas tank pump has high energy conversion rate can be further realized. When the gas flows from the top to the bottom of the valve 8, the gas will drive the valve 8 to rotate towards the center of the airflow channel 9, so that the valve 8 rotates towards the center of the airflow channel 9 and is mutually aggregated, thereby playing a role of blocking the airflow channel 9, therefore, when the valves 8 are mutually aggregated, the valve is in a closed state, and the purpose of reverse check is realized, the distance from the top to the bottom of the valve 8 is greater than the radius of the airflow channel 9, when the valves 8 are aggregated, the side edge of any valve 8 is tightly abutted with the side edge of the adjacent valve flap membrane 8 to form a closed surface for blocking the circulation of the airflow channel 9, therefore, when the valves 8 are aggregated, the valve is in a closed state to block the gas from passing through, when the valves 8 are aggregated, because the distance from the top to the bottom of the valve 8 is greater than the radius of the airflow channel 9, therefore, in the process of closing and rotating any one valve 8, the valve clack membrane 8 can abut against other valve 8 without rotating to a state parallel to the cross section of the airflow channel 9 to form a closed surface, so that the rotating amplitude of the valve 8 is reduced, and the purpose of reducing the back stepping amount in closing is further achieved.
For convenience of technical solution, the nth pressure cylinder in the gas flow direction is an n-stage pressure cylinder, wherein n is greater than or equal to 2, the specific stages of pressure cylinders 4 in the gas flow direction are sequentially named as a first-stage pressure cylinder 4-1, a second-stage pressure cylinder 4-2, a third-stage pressure cylinder 4-3, a fourth-stage pressure cylinder 4-4 and an n-stage pressure cylinder 4-n, wherein n is represented as the nth pressure cylinder in the gas flow direction, the higher the stage, the smaller the volume of the accommodating cavity of the corresponding pressure cylinder, and the greater the pressure in the corresponding pressure cylinder 4.
The number of the n stages of pressure cylinders is at least two, wherein, two are preferable, namely, the high-pressure gas tank pump specifically illustrated in the embodiment has two pressure cylinder groups with the same stage number, so as to perform detailed description of the technical scheme.
In this embodiment, specifically, as shown in fig. 2 and fig. 6, n is preferably equal to four, that is, in this embodiment, a high-pressure gas tank pump with a four-stage pressure cylinder, that is, a structural diagram of a four-stage two-group high-pressure gas tank pump is specifically used to explain a specific technical solution of this embodiment, and the structural principles of other high-pressure gas tank pumps, such as a two-stage two-group high-pressure gas tank pump, a two-stage four-group high-pressure gas tank pump, or a six-stage two-group high-pressure gas tank pump, are similar, and are not described herein again.
Referring to the figure, the four-stage two-group high-pressure gas pressure pump is provided with two first-stage pressure cylinders 4-1, two second-stage pressure cylinders 4-2, two third-stage pressure cylinders 4-3 and two fourth-stage pressure cylinders 4-4, wherein a gas inlet 6 of the first-stage pressure cylinder 4-1 is communicated with a low-pressure gas inlet pipe 1, a gas outlet 7 of the fourth-stage pressure cylinder is connected with a high-pressure gas outlet pipe 2, and the first-stage pressure cylinders 4-1, the second-stage pressure cylinders 4-2, the third-stage pressure cylinders 4-3 and the fourth-stage pressure cylinders 4-4 are sequentially connected in series end to end (with the gas inlet as the first end and the gas outlet as the tail).
As can be seen from the above, in the present embodiment, the definition of the number of stages is: the definition of the nth specific pressure cylinder whose volume becomes smaller in the flow direction of the gas, i.e. the number of stages, is not only reflected in the sequence but also in its corresponding volume change.
Preferably, referring to fig. 2, 6 and 7, the receiving cavities of the pressure cylinders 4 are all cylindrical, and the center lines of the cylindrical receiving cavities of the pressure cylinders 4 are arranged in parallel, which facilitates the connection of the transmission rod 3 with the piston 5 inside the pressure cylinder 4.
Preferably, with reference to fig. 2 and 6, the central axis of the transmission rod 3 is arranged parallel to the central axis of the receiving chamber of the pressure cylinder 4, the transmission rod 3 is provided with a plurality of push-pull rods 31 parallel to the transmission rod 3, and the ends of the push-pull rods 31 are connected to the piston 5.
Wherein, the lengths of the pressure cylinders 4 are the same, and the lengths of the push-pull rods 31 are the same and are matched with the lengths of the pressure cylinders 4, because one end of each push-pull rod 31 directly acts on the corresponding piston 5, and the other end of each push-pull rod 31 is connected to the same transmission rod 3, when the transmission rod 3 reciprocates, the distance of the transmission rod 3 is the distance of the push-pull rod 31, and the push-pull rods 31 act on the pressure cylinders with different volumes, therefore, the purpose that the push-pull rods 31 act on all the pressure cylinders 4 in the same group synchronously can be realized, that is, the purpose of multi-stage synchronization is realized, and further, the purpose of high-efficiency compression and gas transmission is realized, and the central axis of the transmission rod 3 is arranged in parallel to the central line of the containing cavity of the pressure cylinder 4, so that the push-pull rod 31 parallel to the transmission rod 3 can act on the piston 5 vertically, and then make push-and-pull rod 31 all can reach the equal purpose to the thrust and the pulling force of piston 5, do benefit to stable compression and transmission high-pressure gas, the perpendicular effect also can play the effect of guaranteeing push-and-pull rod 31 effort maximize simultaneously.
In this embodiment, the connection structure between the multiple pressure cylinders 4 is in an end-to-end serial connection form, and is not in a mutually nested form, so that the number of stages of the pressure cylinders 4 in this embodiment can be further increased, and as the number of stages increases, the volume of the corresponding pressure cylinder decreases in an inverse proportion, that is, the pressure inside the pressure cylinder 4 increases as the number of stages increases, so as to achieve the purpose of further increasing the pressure value of the high-pressure gas tank pump, and in the flow direction of the same gas, the pistons 5 on different pressure cylinders 4 are synchronously driven by the push-pull rod 31 on the same transmission rod 3, and the gas of the previous pressure cylinder is discharged and then directly and simultaneously sucked into the receiving cavity of the next pressure cylinder, so as to perform further compression operation, that the suction or discharge operation between any two pressure cylinders is performed simultaneously, so as to finally achieve the purpose of multi-stage synchronization, the purpose of coaxial same-level gapless compression is achieved, and the timeliness of the output high-pressure gas is improved.
Preferably, referring to fig. 1 and 2, the hydraulic actuator further comprises a rigid housing 13, a plurality of pressure cylinders 4 are arranged in the rigid housing 13 in a mutually parallel manner, a sliding groove 14 penetrating through the rigid housing 13 is formed in the middle of the rigid housing 13, the transmission rod 3 is slidably arranged in the sliding groove 14, the length of the sliding groove 14 is the width of the whole rigid housing 13, and the long-lead sliding groove 14 can play a role in improving the operation stability of the transmission rod 14, so that the transmission rod 3 is stressed well.
Specifically, referring to fig. 2 and 6, the driving rod 3 passes through the rigid housing 13 through the sliding slot 14, and the rod segments at both ends of the driving rod 3 after passing through the rigid housing 13 are provided with push-pull rods 31 parallel to the driving rod 3.
Preferably, two n-stage pressure cylinders with the same number of stages are arranged on the rigid shell 13 in an opposite manner, that is, the opening directions of any two pressure cylinders 4 with the same number of stages are arranged on the rigid shell 13 in an opposite manner, that is, in this embodiment, two primary pressure cylinders 4-1 are arranged on the rigid shell 13 in an opposite manner, and the position relationship between the other pressure cylinders 4 with the same number of stages is also the same, so that the pistons 5 on the pressure cylinders with the same number of stages are controlled by the push-pull rods 31 on the rod segments at the two ends of the transmission rod 3 respectively, and when the transmission rod 3 reciprocates, the action states of any two pressure cylinders with the same number of stages are just opposite, that is, referring to fig. 6, taking the action of two primary pressure cylinders 4-1 as an example, because two primary pressure cylinders 4-1 are arranged on the rigid shell 13 in an opposite manner, the pistons 5 on the two primary pressure cylinders 4-1 are controlled by the push-pull rods 31 on the rod segments at the two ends of the transmission rod 3 respectively, therefore, when one primary pressure cylinder 4-1 is in the exhaust action state, the other primary pressure cylinder 4-1 is in the air suction action state, and the arrangement enables the pressure cylinders with the same number of stages to be in the opposite action state, and the pressure cylinders only have two action states, namely the exhaust action state and the air suction action state, in the normal operation process, therefore, the pressure cylinders with the same number of stages are arranged in a reverse manner and are respectively controlled by the push-pull rods 31 on the rod sections at the two ends of the transmission rod 3, so that the high-pressure gas tank pump can achieve the purpose of continuously pumping high-pressure gas, and simultaneously can play a role in balancing the stress of all points of the transmission rod.
Preferably, referring to fig. 7, the push-pull rods 31 are symmetrically distributed around the transmission rod 3 to further achieve the purpose of moment balance.
Preferably, the ratio of the radii between the receiving chambers of any two adjacent pressure cylinders 4 in the gas flow direction is equal, namely:
k is a constant, namely K is a step radius ratio, and Rn is the radius of the containing cavity of the nth pressure cylinder along the gas flowing direction.
Preferably, the ratio of the radii between the receiving chambers of any two adjacent pressure cylinders 4 in the gas flow direction is 1.5-2.5, namely: k is more than or equal to 1.5 and less than or equal to 2.5.
Preferably, the number of pressure cylinders 4 is set to 2 to 12, i.e. in terms of structural design, preferably two-stage one, two-stage two, two-stage four-stage two, six-stage two, etc., although it may also be more than 12, for example four-stage four.
Preferably, referring to fig. 2, a matching convex part 51 matched with the inner cavity of the one-way flow guide part in the closed state is arranged at a position corresponding to the air outlet 7 on the piston 5, when the pressure cylinder 4 is in a state of extruding gas, the matching convex part 51 on the piston 5 can enter a space surrounded by the valve 8 on the air outlet 7 to play a role of reducing gas residue in the pressure cylinder, and the arrangement of the matching convex part 51 can realize that the gas residue in the cylinder is controlled within 0.5%.
Preferably, referring to fig. 2, a matching concave cavity 52 matched with the shape of the one-way flow guide in the closed state is arranged at a position corresponding to the air inlet 6 on the piston 5, when the piston 5 performs extrusion air exhaust in the pressure cylinder 4, the piston 5 is close to the cylinder bottom of the pressure cylinder, and the valve 8 at the air inlet 6 is arranged inside the pressure cylinder 4, so that the matching concave cavity 52 matched with the shape of the one-way flow guide in the closed state is arranged on the corresponding inner surface of the piston, and when the piston 5 approaches the cylinder bottom of the pressure cylinder 4 in the extrusion air exhaust process, the one-way flow guide in the closed state enters the matching concave cavity 52, so that the piston 5 can fully fit the cylinder bottom of the pressure cylinder 4 to ensure full air exhaust.
Preferably, referring to fig. 2 and 5, the device further comprises a driving motor 10 and an eccentric disc 11, one end of the driving rod 3 is provided with a central sliding slot 32 perpendicular to the central axis of the driving rod 3, an output shaft of the driving motor 10 is connected with the eccentric disc 11, the eccentric disc 11 is provided with an eccentric shift lever 12, the eccentric shift lever 12 is slidably arranged in the central sliding slot 32, wherein, the eccentric deflector rod 12 is arranged on the eccentric disc 11 and is eccentric with the output shaft of the driving motor 10, since the central slide 32 is perpendicular to the central axis of the transmission rod 3, and the eccentric shift lever 12 slides in the central slide 32, the central slide 32 thus serves to eliminate the effect of the thrust of the eccentric dog 12 in a direction perpendicular to the axis of the transmission rod 3, thereby achieving the purpose of converting the rotating motion of the eccentric deflector rod 12 into the reciprocating linear motion of the transmission rod 3, therefore, the eccentric disc 11 driven by the driving motor 10 achieves the purpose of driving the transmission rod 3 to reciprocate.
Specifically, in this embodiment, the driving device further includes a reduction gearbox 18, an output shaft of the driving motor 10 is connected to an input shaft of the reduction gearbox 18, an output shaft of the reduction gearbox 18 is connected to the eccentric disc 11 in an installing manner to play a role in speed regulation, wherein the driving motor 10 and the reduction gearbox 18 are both installed on an outer side wall of the rigid casing 13, and an integrated structure is facilitated.
Preferably, referring to fig. 1,2 and 5, a mechanism box 15 is disposed on the rigid housing 13, the eccentric disc 11 and the central sliding slot 32 on the transmission rod 3 are movably mounted in the mechanism box 15, and the mechanism box 15 is used for mounting structural components such as the eccentric disc 11 and the like which drive the transmission rod 3 to reciprocate, so as to achieve a stable structure.
Preferably, referring to fig. 3,4, 8 and 9, the projection of the valve flap membrane 8 on the longitudinal section of the gas flow channel 9 is isosceles triangle, and the valve flaps 8 are in cone or pyramid shape when they are combined, wherein in this embodiment, the longitudinal section of the gas flow channel 9 is the section of the flow channel parallel to the flow direction of the gas, and the cross section of the gas flow channel 9 is the section of the gas flow channel 9 perpendicular to the flow direction of the fluid medium, because the sealing surface formed by the valve flap membranes 8 being in close contact with each other is in cone or pyramid shape when in the closed state, the compression strength of the sealing surface in the axial direction of the gas flow channel 9 is greatly improved when in the closed state, and the connection between the valve flaps 8 is tighter when the fluid pressure is higher when the gas flows back, the sealing performance of the sealing surface is higher, and the high-pressure gas tank pump has the characteristic of high non-return sealing performance.
Preferably, referring to fig. 3,4, 8 and 9, the valve valves 8 are provided with reinforcing steel plates 16 whose shapes are matched with the shapes of the valve valves 8, the reinforcing steel plates 16 can play a role in improving the structural strength of the valve valves 8 themselves, and the valve valves 8 are prevented from being deformed due to bending deformation under impact and extrusion of high-pressure gas, so as to ensure the use stability of the one-way flow guide member, and under the combined effect of the reinforcing steel plates 16 and the valve valves 8, the high-pressure resistance of the one-way flow guide member is further improved, the stability is stronger, the material is steel, the strength is high, and the corrosion resistance is also strong.
Preferably, referring to fig. 3,4, 8 and 9, the single-line flow guide piece further includes a peripheral film 17 sleeved outside the valve valves 8, the peripheral film 17 is cylindrical or prismatic, the bottom of the peripheral film 17 is connected with the bottom of the valve clack film 8, in the closing process, the peripheral film 17 is driven by high-pressure gas flowing in the reverse direction to wrap around and tightly adhere to the outer surface of the valve valves 8, the peripheral film 17 is tightly adhered to the valve valves 8, so that the valve valves 8 can be further sealed, a double sealing effect is achieved, the sealing stability of the single-line flow guide piece is further improved, and in the opening state, the peripheral film 17 is pushed by the high-pressure gas to expand into a cylindrical structure or a prismatic structure, so that the barrier-free passing purpose is achieved.
The working principle is as follows: referring to fig. 2 and 6, the driving motor 10 drives the transmission rod 3 to reciprocate, when the push-pull rod 31 in the first-stage pressure cylinder 4-1 drives the piston 5 to perform air suction, low-pressure gas enters the first-stage pressure cylinder 4-1 from the air inlet pipe 1, the odd-numbered pressure cylinders in the same group perform air suction, and the even-numbered pressure cylinders in the same group perform air exhaust; meanwhile, the other group of pressure cylinders can do opposite actions, so that the aim of continuously sucking and exhausting is fulfilled, and the aim of compressing gas can be fulfilled as the volume of the corresponding pressure cylinder is smaller as the number of stages is higher.
The beneficial effects of this embodiment: the valve valves are arranged on the air inlet and/or the air outlet and form an integral one-way flow guide part in a surrounding way, the aim of one-way opening or one-way non-return is realized by utilizing the phase separation or the phase polymerization of the valve valves, in the opening process, high-pressure air can directly flow through gaps among the valve valves, the directly flowing air cannot be blocked by the valve valves, so that the resistance coefficient is reduced, the air flowing efficiency is improved, and the valve valves can be in a state parallel to the air flowing direction after being completely opened, so that the one-way flow guide part has a very low resistance coefficient in a completely opened state, the high-pressure air box pump can be ensured to have a high energy conversion rate, the high-pressure air box pump has an ultrahigh pressure application prospect, the valve valves have small rotating amplitude, and the function of effectively reducing the back-stepping amount of air can be realized, the valve in the closed state is not vertical to the airflow channel, so that the opening speed of the valve is increased in the opening process, and the opening response speed of the one-way flow guide piece is increased; the pressure cylinders with the same series are arranged in a back-to-back mode and are controlled by the corresponding push-pull rods on the rod sections at the two ends of the transmission rod respectively, so that the high-pressure gas tank pump can achieve the purpose of pumping high-pressure gas in a multistage synchronous and continuous mode, the matched concave cavity plays a role in ensuring that the piston can fully fit the cylinder bottom of the pressure cylinder in the exhaust process, sufficient exhaust is ensured, and the matched convex piece plays a role in reducing the residual quantity of gas in the pressure cylinder.
In this embodiment, taking the comparison between the air compressor and the high-pressure gas tank pump as an example, the following table 9 is obtained, wherein the calculation formula of the total residual quantity and the total leakage loss ratio is as follows:
wherein S isn: total ratio (%) of total residue to leakage of n-stage pressure cylinder, an: the ratio (%) of the cylinder residual volume to the leakage volume of the n-stage pressure cylinder, P1n: maximum inlet pressure (Mpa), P, of n-stage pressure cylinder2n: maximum outlet pressure (Mpa), S of n-stage pressure cylindern-1: the total residual to leakage ratio (%) of the n-1 stage cylinder.
Table 1: energy efficiency comparison estimation meter for high-pressure gas tank pump and single-stage air compressor
Continuing with Table 1:
description of the drawings: the existing air compressor adopts a lifting check valve, the resistance coefficient of the air compressor is 10-12, and the resistance coefficient of the high-pressure air box pump is 0.3-0.5.
Wherein, when the air is pressurized from 0.1Mpa to 2Mpa, the volume is changed to 5 percent of the original volume, the cylinder residue of the prior air compressor is more than 1 percent, in this embodiment, when the cylinder residual amount is 1%, 20% of the gas remains in the pneumatic cylinder of the air compressor and cannot be discharged, and similarly, when the air is pressurized from 0.1MPa to 4, 6, 9 and 10MPa, the cylinder residual amounts, calculated as 1%, will be 40%, 60%, 90%, 100% respectively, thereby lowering the pressure output value of the prior air compressor, and as can be seen from the above table 1 and the following table 1, the total residual quantity and leakage loss of the high-pressure gas tank pump are far smaller than those of the air compressor, so that the comprehensive efficiency and the comprehensive efficiency ratio of the high-pressure gas tank pump are very high, and the high-pressure gas tank pump has very high ultrahigh application value.
In this example, the pressure multiple was calculated on the basis of a basic data set including K of 1.5, n of 1,2,3,4,5,6 and a cylinder radius of 0.8m of the primary cylinder.
Specifically, the calculation formula of the theoretical pressure amplification factor of the high-pressure gas tank pump is as follows:
B＝(K2)n
wherein B is a theoretical pressure amplification factor, n is the number of stages of the high-pressure gas tank pump, and K is a stage radius ratio.
The following table for calculating the pressure multiple of the high-pressure gas tank pump was obtained:
TABLE 2
| Number of | Level | 1 | |
|
4 | Grade | 5 | |
| Volume (m3) | 0.40 | 0.1786 | 0.0794 | 0.0353 | 0.0157 | 0.0070 | ||
| Cylinder diameter r (m) | 0.8 | 0.533 | 0.356 | 0.237 | 0.158 | 0.105 | ||
| Cylinder stroke S (m) | 0.2 | 0.2 | 0.2 | 0.2 | 0.2 | 0.2 | ||
| Step radius ratio k | 1.5 | 1.5 | 1.5 | 1.5 | 1.5 | |||
| Ratio of cylinder residual volume to leakage volume (%) | 1 | 1 | 1 | 1 | 1 | 1 | ||
| Maximum inlet pressure (Mpa) | 0.1 | 0.225 | 0.506 | 1.139 | 2.563 | 5.767 | ||
| Outlet pressure (Mpa) | 0.225 | 0.495 | 1.088 | 2.390 | 5.248 | 11.515 | ||
| Total residue to leakage loss (%) | 2.25 | 4.5 | 6.75 | 9.00 | 11.25 | 13.50 | ||
| Actual inlet pressure (Mpa) | 0.220 | 0.483 | 1.062 | 2.332 | 5.118 | |||
| Pressure multiple B | 2.25 | 4.95 | 10.63 | 22.31 | 45.68 | 91.22 |
TABLE 32 MPa calculation table
Table 4: 4Mpa calculation table
| Number of | Level | 1 | |
|
4 stage |
| Volume (m3) | 0.40 | 0.1786 | 0.0598 | 0.231 | |
| Cylinder diameter r (m) | 0.8 | 0.533 | 0.3009 | 0.192 | |
| Cylinder stroke S (m) | 0.2 | 0.2 | 0.2 | 0.200 | |
| Step radius ratio k | 2.15 | 1.610 | 1.610 | ||
| Ratio of cylinder residual volume to leakage volume (%) | 1 | 1 | 1 | 1 | |
| Maximum inlet pressure (Mpa) | 0.1 | 0.462 | 0.672 | 1.742 | |
| Outlet pressure (Mpa) | 0.462 | 2.038 | 1.651 | 4.163 | |
| Total residue to leakage loss (%) | 4.6225 | 9.25 | 7.78 | 10.37 | |
| Actual inlet pressure (Mpa) | 0.441 | 0.637 | 1.606 |
Table 5: 6Mpa calculation table
Table 6: 9Mpa calculation table
| |
|
|
4 stage | |
| Capacity (M3) | 0.40 | 0.1269 | 0.0400 | 0.0126 |
| Jar diameter r (M) | 0.8 | 0.449 | 0.252 | 0.142 |
| Cylinder stroke S (M) | 0.2 | 0.200 | 0.200 | 0.200 |
| Step radius ratio n | 1.780 | 1.780 | 1.780 | |
| Ratio of cylinder residual volume to leakage volume (%) | 1 | 1.000 | 1.000 | 1.000 |
| Maximum inlet pressure (Mpa) | 0.1 | 0.317 | 1.004 | 3.181 |
| Outlet pressure (Mpa) | 0.31684 | 0.972 | 2.979 | 9.120 |
| Total residue to leakage loss (%) | 3.1684 | 6.34 | 9.51 | 12.67 |
| Actual inlet pressure (Mpa) | 0.307 | 0.940 | 2.878 |
Table 7: 20Mpa calculation table
| |
|
|
4 stage | |
| Capacity (M3) | 0.40 | 0.1036 | 0.0267 | 0.0069 |
| Jar diameter r (M) | 0.8 | 0.406 | 0.206 | 0.105 |
| Cylinder stroke S (M) | 0.2 | 0.200 | 0.200 | 0.200 |
| Step radius ratio n | 1.970 | 1.970 | 1.970 | |
| Ratio of cylinder residual volume to leakage volume (%) | 1 | 1.000 | 1.000 | 1.000 |
| Maximum inlet pressure (Mpa) | 0.1 | 0.388 | 1.506 | 5.845 |
| Outlet pressure (Mpa) | 0.38809 | 1.448 | 5.391 | 20.043 |
| Total residue to leakage loss (%) | 3.8809 | 7.76 | 11.64 | 15.52 |
| Actual inlet pressure (Mpa) | 0.373 | 1.389 | 5.165 |
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.
It will be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (16)
1. The high-pressure gas tank pump is characterized by comprising a low-pressure gas inlet pipe (1), a high-pressure gas exhaust pipe (2) and a transmission rod (3) capable of making reciprocating motion along the axis of the high-pressure gas inlet pipe, wherein a plurality of pressure cylinders (4) are connected between the low-pressure gas inlet pipe (1) and the high-pressure gas exhaust pipe (2) in series, the volumes of accommodating cavities of the pressure cylinders (4) are sequentially reduced along the gas flowing direction, pistons (5) are arranged in the pressure cylinders (4), the pistons (5) are connected with the transmission rod (3), gas inlets (6) and gas outlets (7) are arranged in the pressure cylinders (4), and one-way flow guide pieces are arranged on the gas inlets (6) and/or the gas outlets (7);
one-way water conservancy diversion spare has that a plurality of bottoms meet in proper order and close annular valve (8), and is a plurality of the inner space that forms is closed mutually in valve (8) forms airflow channel (9) that air feed circulation, the top to the distance of bottom of valve (8) is greater than airflow channel (9)'s radius, a plurality of for open mode when valve (8) phase separation to the air feed passes through, a plurality of be closed state when valve (8) phase polymerization, in order to block gas and pass through, a plurality of when valve (8) phase polymerization, arbitrary one the side of valve (8) is rather than adjacent the side looks inseparable butt of valve (8).
2. A high-pressure gas tank pump according to claim 1, characterized in that the receiving chambers of a number of said pressure cylinders (4) are cylindrical and the centre lines of the cylindrical receiving chambers of a number of said pressure cylinders (4) are arranged in parallel.
3. A high-pressure gas tank pump according to claim 2, characterized in that the central axis of the transmission rod (3) is arranged parallel to the central axis of the receiving chamber of the pressure cylinder (4), the transmission rod (3) is provided with a plurality of push-pull rods (31) parallel to the transmission rod (3), the ends of the push-pull rods (31) are connected to the pistons (5).
4. A high-pressure gas tank pump according to any one of claims 1 to 3, characterized in that the ratio of the radii between the receiving chambers of any two adjacent pressure cylinders (4) in the gas flow direction is equal.
5. A high-pressure gas tank pump according to claim 4, characterized in that the ratio of the radii between the receiving chambers of any two adjacent pressure cylinders (4) in the gas flow direction is 1.5-2.5.
6. A high-pressure gas tank pump according to any one of claims 1 to 3, characterized in that the number of pressure cylinders (4) is set to 2 to 12.
7. A high-pressure gas tank pump according to any one of claims 1 to 3, further comprising a driving motor (10) and an eccentric disc (11), wherein one end of the driving rod (3) is provided with a central sliding groove (32) perpendicular to the central axis of the driving rod (3), an output shaft of the driving motor (10) is connected with the eccentric disc (11), the eccentric disc (11) is provided with an eccentric shift lever (12), and the eccentric shift lever (12) is slidably disposed in the central sliding groove (32).
8. A high-pressure gas tank pump according to claim 3, characterized in that it further comprises a rigid housing (13), a plurality of said pressure cylinders (4) being arranged in said rigid housing (13), a sliding groove (14) extending through said rigid housing (13) being provided in the middle of said rigid housing (13), said transmission rod (3) being slidably arranged in said sliding groove (14).
9. The high-pressure gas tank pump as claimed in claim 8, characterized in that the drive rod (3) penetrates through the rigid housing (13) via the sliding groove (14), the push-pull rod (31) parallel to the drive rod (3) is arranged on both end rod sections of the drive rod (3) after penetrating out of the rigid housing (13), and the nth pressure cylinder in the gas flow direction is an n-stage pressure cylinder, wherein n is greater than or equal to 2.
10. A high-pressure gas tank pump according to claim 9, wherein the number of said n-stage pressure cylinders having the same number of stages is at least two.
11. A high-pressure gas tank pump according to claim 9 or 10, characterized in that any two of said n-stage pressure cylinders of the same order are arranged opposite each other on said rigid housing (13).
12. A high-pressure gas tank pump according to any one of claims 1 to 3, characterized in that the projection of the valve valves (8) onto a longitudinal section of the gas flow channel (9) is in the form of an isosceles triangle, several of the valve valves (8) being in the form of a cone or pyramid when they converge.
13. A high-pressure gas tank pump according to claim 1, characterized in that several valve valves (8) are provided with a reinforced steel plate (16) having a shape adapted to the shape of the valve valves (8).
14. A high-pressure gas tank pump according to claim 12, characterized in that it further comprises a peripheral membrane (17) fitted over the outside of said valve means (8), said peripheral membrane (17) being cylindrical or prismatic in shape, the bottom of said peripheral membrane (17) being connected to the bottom of said valve means (8).
15. A high-pressure gas tank pump according to any one of claims 1 to 3, characterized in that a mating male part (51) adapted to the inner cavity of the one-way flow guide in the closed state is provided at a position on the piston (5) corresponding to the outlet (7).
16. A high-pressure gas tank pump according to any one of claims 1 to 3, characterized in that the piston (5) is provided with a matching cavity (52) at a position corresponding to the gas inlet (6) that is adapted to the outer shape of the one-way flow guide in the closed state.
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| CN112832989A (en) * | 2021-02-08 | 2021-05-25 | 曾昭达 | A high pressure gas tank pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112832989A (en) * | 2021-02-08 | 2021-05-25 | 曾昭达 | A high pressure gas tank pump |
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Effective date of registration: 20221123 Address after: Room 414, Floor 4, Building A2, Innovation and Entrepreneurship Science Park, Zhaoqing Hi tech Zone, No. 29, Jianshe Road, Zhaoqing Hi tech Zone, Guangdong Province, 526000 Patentee after: Guangdong Xinstable Energy Control Technology Research Co.,Ltd. Address before: Room 1002, No.11 Jifu street, Baiyun District, Guangzhou, Guangdong 510440 Patentee before: Zeng Zhaoda |
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Effective date of registration: 20231029 Address after: Unit 500, Building 2, No. 101 Daxue Road, Tangjiawan Town, High tech Zone, Zhuhai City, Guangdong Province, 519000 Patentee after: Guangdong Xinwen Valve Flow Power Co.,Ltd. Address before: Room 414, Floor 4, Building A2, Innovation and Entrepreneurship Science Park, Zhaoqing Hi tech Zone, No. 29, Jianshe Road, Zhaoqing Hi tech Zone, Guangdong Province, 526000 Patentee before: Guangdong Xinstable Energy Control Technology Research Co.,Ltd. |
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