CN110701040B - Static pressure support for spherical pump rotor - Google Patents
Static pressure support for spherical pump rotor Download PDFInfo
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- CN110701040B CN110701040B CN201911060871.1A CN201911060871A CN110701040B CN 110701040 B CN110701040 B CN 110701040B CN 201911060871 A CN201911060871 A CN 201911060871A CN 110701040 B CN110701040 B CN 110701040B
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- flow channel
- liquid flow
- bearing groove
- liquid
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- 230000003068 static effect Effects 0.000 title abstract description 14
- 239000007788 liquid Substances 0.000 claims abstract description 186
- 230000002706 hydrostatic effect Effects 0.000 claims abstract description 12
- 238000000034 method Methods 0.000 abstract description 7
- 239000012530 fluid Substances 0.000 description 43
- 239000004696 Poly ether ether ketone Substances 0.000 description 16
- JUPQTSLXMOCDHR-UHFFFAOYSA-N benzene-1,4-diol;bis(4-fluorophenyl)methanone Chemical compound OC1=CC=C(O)C=C1.C1=CC(F)=CC=C1C(=O)C1=CC=C(F)C=C1 JUPQTSLXMOCDHR-UHFFFAOYSA-N 0.000 description 16
- 229920002530 polyetherether ketone Polymers 0.000 description 16
- 238000007789 sealing Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 9
- 238000010992 reflux Methods 0.000 description 9
- 238000000576 coating method Methods 0.000 description 8
- 238000001816 cooling Methods 0.000 description 7
- 239000011248 coating agent Substances 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 230000008093 supporting effect Effects 0.000 description 5
- 239000000758 substrate Substances 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000002035 prolonged effect Effects 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000110 cooling liquid Substances 0.000 description 2
- 238000001125 extrusion Methods 0.000 description 2
- 238000001746 injection moulding Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000011159 matrix material Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C9/00—Oscillating-piston machines or pumps
- F04C9/002—Oscillating-piston machines or pumps the piston oscillating around a fixed axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The patent discloses a static pressure support of a spherical pump rotor, wherein the static pressure support is arranged between two parallel side surfaces of a sliding shoe (403) and a sliding groove (601); the hydrostatic support comprises a first liquid flow channel (404), a second liquid flow channel (405) and liquid pressure-bearing grooves, wherein the first liquid flow channel (404) and the second liquid flow channel (405) are arranged on the turntable (4), the liquid pressure-bearing grooves are arranged on two parallel sides of the sliding shoe (403), the first liquid flow channel inlet (4041) is communicated with one working chamber (1001), the second liquid flow channel inlet (4051) is communicated with the other working chamber (1001), and the first liquid flow channel outlet (4042) and the second liquid flow channel outlet (4052) are respectively communicated with the liquid pressure-bearing grooves on two parallel sides of the sliding shoe (403); the spherical pump has the advantages that unbalanced force in the running process of the spherical pump is eliminated, gaps between the matching surfaces are ensured, and the power consumption of the spherical pump is reduced.
Description
Technical Field
The patent relates to a variable displacement mechanism, in particular to a hydrostatic support of a spherical pump rotor.
Background
The spherical pump is a variable capacity mechanism with a brand new structure, which is newly invented in recent years, and has the advantages of no air inlet/outlet valve, less moving parts, surface contact among the moving parts, and surface sealing structure, so that the sealing is reliable, and the like, and high pressure and structure miniaturization can be realized. Spherical pumps are now used in practice for a number of applications, being new constructions for pumps. However, since there is a fixed angle between the piston axis and the main shaft of the ball pump, the pressures in the two working chambers change reciprocally, and when one working chamber is at high pressure, the other working chamber is at low pressure, which causes the piston and the turntable to deflect to one side of the low pressure, the spherical surface of the cylinder is extruded, the gap between the turntable and the spherical surface of the cylinder is reduced, the oil film or the water film is destroyed, the friction force is increased, the power consumption is increased, and the rotor and the sliding shoe are abnormally worn.
Disclosure of Invention
The invention aims to design a static pressure support of a spherical pump rotor, wherein the static pressure support is added on a sliding shoe of the spherical pump rotor, and unbalanced force generated by the spherical pump in the running process of the spherical pump is balanced through liquid pressure, so that running power consumption is reduced, and the service life of the spherical pump is prolonged.
The technical scheme of the invention is that the static pressure support of the spherical pump rotor is characterized in that: the static pressure support comprises a first liquid flow channel, a second liquid flow channel and liquid pressure-bearing grooves, wherein the first liquid flow channel and the second liquid flow channel are arranged on the turntable, the liquid pressure-bearing grooves are arranged on two parallel side surfaces of the sliding shoe, the inlet of the first liquid flow channel is communicated with one working chamber, the inlet of the second liquid flow channel is communicated with the other working chamber, and the outlet of the first liquid flow channel and the outlet of the second liquid flow channel are respectively communicated with the liquid pressure-bearing grooves on the two parallel side surfaces of the sliding shoe; a sliding shoe lining plate is arranged between the two parallel side surfaces of the sliding shoe and the side surface attached to the sliding groove; the two parallel side surfaces of the sliding shoe are adhered to the sliding shoe lining plates on the two sides and slide back and forth along the surfaces of the sliding shoe lining plates in the sliding groove; the static pressure supports are arranged between two parallel side surfaces of the sliding shoe and the sliding shoe lining plate;
the first liquid flow channel inlet is arranged on the upper end surface of the turntable and communicated with the working chamber, the first liquid flow channel outlet is arranged on one of two parallel side surfaces of the sliding shoe, and the first liquid flow channel inlet and the first liquid flow channel outlet are respectively positioned on two sides of a plane parallel to the two parallel side surfaces of the sliding shoe where the axis of the turntable is positioned; the second liquid flow channel inlet is arranged on the upper end surface of the turntable and communicated with the other working chamber, the second liquid flow channel outlet is arranged on the other side surface of the two parallel side surfaces of the sliding shoe, and the second liquid flow channel inlet and the second liquid flow channel outlet are respectively positioned on two sides of a plane parallel to the two parallel side surfaces of the sliding shoe where the axis of the turntable is positioned;
the first liquid pressure-bearing groove and the second liquid pressure-bearing groove are arranged on two parallel side surfaces of the sliding shoe, the first liquid flow channel outlet is communicated with the first liquid pressure-bearing groove, the second liquid flow channel outlet is communicated with the second liquid pressure-bearing groove, the cross-sectional dimension of the first liquid pressure-bearing groove is larger than that of the first liquid flow channel outlet, the cross-sectional dimension of the second liquid pressure-bearing groove is larger than that of the second liquid flow channel outlet, and the surfaces of the first liquid pressure-bearing groove and the second liquid pressure-bearing groove are slightly lower than the planes of two sides of the sliding shoe;
the liquid bearing groove comprises a first multistage bearing groove and a second multistage bearing groove which are arranged on two parallel sides of the sliding shoe, the outlet of the first liquid flow channel is communicated with the first multistage bearing groove, the outlet of the second liquid flow channel is communicated with the second multistage bearing groove, the cross-sectional size of the first multistage bearing groove is larger than that of the outlet of the first liquid flow channel, the cross-sectional size of the second multistage bearing groove is larger than that of the outlet of the second liquid flow channel, and the surfaces of the first multistage bearing groove and the second multistage bearing groove are slightly lower than the planes on two sides of the sliding shoe; the first multistage pressure-bearing groove and the second multistage pressure-bearing groove both comprise a basic pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves, the basic pressure-bearing groove is arranged in the center of two parallel side surfaces of the sliding shoe, the bottom of the basic pressure-bearing groove is communicated with the first liquid flow channel outlet or the second liquid flow channel outlet, the plurality of auxiliary pressure-bearing grooves are respectively arranged on the periphery of the basic pressure-bearing groove, and the plurality of auxiliary pressure-bearing grooves sequentially encircle the periphery of the basic pressure-bearing groove;
the liquid pressure-bearing grooves can be round grooves or rectangular grooves, and the multi-stage liquid pressure-bearing grooves can be multi-stage round grooves or multi-stage rectangular grooves;
the invention has the advantages that: the unbalanced force caused by asymmetric compression of the two working chambers in the rotation process of the rotor is eliminated, the static pressure support is arranged on the sliding shoe, and the larger balanced force can be obtained on the turntable due to the leverage; the gaps among the spherical surface of the piston, the spherical surface of the turntable and the spherical inner cavity are ensured to be uniform, and friction loss and friction force are reduced; simultaneously, the friction force between the sliding shoes and the sliding grooves is reduced; the unbalanced force in the running process of the spherical pump is eliminated, the gap between the matching surfaces is ensured, the power consumption of the spherical pump is reduced, the cooling and lubricating conditions are improved, and the failure time of parts is prolonged; the device can be used for an oil pump and a water pump.
Drawings
Fig. 1: a spherical pump structure schematic diagram;
fig. 2: A-A in FIG. 1;
fig. 3: FIG. 1 is a sectional view B-B;
fig. 4: a cylinder cover structure schematic diagram;
fig. 5: FIG. 4 is a cross-sectional view C-C;
fig. 6: a cylinder block structure schematic diagram;
fig. 7: FIG. 6 is a sectional view D-D;
fig. 8: a main shaft structure schematic diagram;
fig. 9: FIG. 8 is a sectional view E-E;
fig. 10: a main shaft bracket structure schematic diagram;
fig. 11: FIG. 10 is a sectional view H-H;
fig. 12: FIG. 10 is a cross-sectional view F-F;
fig. 13: a piston structure schematic diagram;
fig. 14: FIG. 13 is a sectional view taken along line L-L;
fig. 15: a turntable structure schematic diagram;
fig. 16: FIG. 15 is a cross-sectional view of K-K;
fig. 17: a perspective view of the turntable structure;
fig. 18: a perspective view of the piston structure;
fig. 19: the multistage liquid pressure-bearing groove is a sliding shoe structure schematic diagram of a rectangular pressure-bearing groove;
fig. 20: FIG. 19 is a cross-sectional view M-M;
fig. 21: the multistage liquid pressure-bearing groove is a skid shoe structure schematic diagram of a circular pressure-bearing groove;
fig. 22: FIG. 21 is a cross-sectional view N-N;
in the figure: 1-a cylinder cover; 2-a piston; 3-a center pin; 4-a turntable; 5-a cylinder; 6-a main shaft; 7-a spindle bracket; 8-bearing; 9-a sealing ring; 10-a slipper liner; 11-cylinder sleeve;
101-a liquid inlet hole; 102-a liquid discharge hole; 103-a cylinder cover split flow channel; 104-a piston shaft hole; 105-liquid inlet kidney-shaped holes; 106-draining kidney-shaped holes; 107-cylinder head return passage; 108-chip removal grooves;
201-a piston base; 202-piston PEEK coating;
401-a turntable substrate; 402-a spin-disk PEEK coating; 403-slipper; 404-a first flow channel; 4041-a first flow channel inlet; 4042-first flow channel outlet; 405-a second flow channel; 4051-a second flow channel inlet; 4052-second flow channel outlet; 406-a first liquid pressure tank; 407-a second liquid pressure tank; 408-a first multilevel rectangular slot; 409-a second multilevel rectangular slot; 410-a first multistage circular groove; 411-a second multi-stage circular groove;
501-a cylinder split flow channel; 502-a cylinder return channel;
601-a chute; 602-spindle overflow aperture; 701-a main shaft bracket reflux groove; 1001-working room.
Detailed Description
As shown in fig. 1 to 3, the spherical pump described in the patent comprises a cylinder cover 1, a piston 2, a turntable 4, a cylinder body 5, a main shaft 6, a main shaft bracket 7 and the like, wherein the cylinder body 5 and the cylinder cover 1 are provided with hemispherical inner cavities, and the cylinder body 5, the cylinder cover 1 and the main shaft bracket 7 are fixedly connected through screws in sequence to form a spherical pump shell with the spherical inner cavities, namely a spherical pump stator; the piston 2, the rotary table 4 and the main shaft 6 are sequentially connected to form a spherical pump rotor; the main shaft bracket 7 is used as a support for the rotation of the main shaft 6, and the main shaft bracket 7 is fixedly connected to the lower end of the cylinder body 5 through a screw; the piston 2 and the rotary table 4 are hinged through the center pin 3, a piston shaft is inserted into the piston shaft hole 104 in the cylinder cover 1, and a sliding shoe 403 at the lower end of the rotary table shaft is inserted into a sliding groove 601 at the upper end of the main shaft 6.
As shown in fig. 4 and 5, a liquid inlet hole 101 and a liquid outlet hole 102 are formed in the upper end surface of the cylinder cover 1, and a liquid inlet kidney-shaped hole 105, a liquid outlet kidney-shaped hole 106 and a piston shaft hole 104 are formed in the inner spherical surface of the cylinder cover 1; the axis of the piston shaft hole 104 passes through the spherical center of the inner spherical surface of the cylinder cover, the orifices of the liquid inlet kidney-shaped hole 105 and the liquid outlet kidney-shaped hole 106 on the inner spherical surface of the cylinder cover 1 are respectively arranged in the annular space perpendicular to the axis of the piston shaft hole 104, the liquid inlet kidney-shaped hole 105 is communicated with the liquid inlet hole 101 at the upper end of the cylinder cover 1, and the liquid outlet kidney-shaped hole 106 is communicated with the liquid outlet hole 102 at the upper end of the cylinder cover 1. The liquid feeding and discharging control is realized through the rotation of the piston 2, and when liquid discharging or liquid feeding is needed in each working chamber, the corresponding working chamber is communicated with the liquid feeding kidney-shaped hole 105 or the liquid discharging kidney-shaped hole 106. In order to prevent abrasive dust generated when the piston shaft rotates in the piston shaft hole 104 from entering between the spherical surface of the piston and the spherical surface in the cylinder cover 1, a chip removal groove 108 is arranged on the spherical surface in the cylinder cover 1, and one end of the chip removal groove 108 is communicated with the liquid inlet kidney-shaped hole 105; the other end of the chip groove 108 extends along the inner spherical surface of the cylinder cover towards the direction of the piston shaft hole 104 and extends to the vicinity of the orifice of the piston shaft hole 104, the section of the chip groove 108 is U-shaped, a U-shaped opening is positioned on the inner spherical surface of the cylinder cover 1, the size of the section (namely the depth and the width of the liquid discharge groove) is based on the principle that the spherical pump does not leak, and the chip groove 108 can be communicated with the piston shaft hole 104 or not communicated with the piston shaft hole 104; in this way, the swarf discharged from the piston shaft bore 104 collects in the junk slots 108 and follows the fluid out of the cylinder as the fluid enters the working chamber 1001.
As shown in fig. 6 and 7, a turntable shaft passing hole penetrating through the outside of the cylinder is arranged at the lower end of the cylinder body 5, and the size of the hole is used for ensuring that the turntable shaft does not interfere with the cylinder body 5 in the rotating process of the turntable 4; the part of the main shaft 6 matched with the lower end of the cylinder body 5 is provided with a cylinder body sleeve hole, the cylinder body sleeve 11 is arranged in the cylinder body sleeve hole and is used for rotating and supporting the upper end of the main shaft 6 (corresponding to a sliding bearing), the axis of the cylinder body sleeve hole and the axis of the cylinder body sleeve 11 are overlapped with the axis of the main shaft 6, the inner diameter of the cylinder body sleeve 11 is matched with the shaft neck at the upper end of the main shaft 6 through the spherical center of the inner spherical surface of the cylinder body, the outer diameter of the cylinder body sleeve 11 is matched with the inner diameter of the cylinder body sleeve hole, the cylinder body sleeve 11 is a cylindrical sleeve, PEEK is used as a material, and through cooling grooves are formed in the outer cylinder and the inner cylinder surface of the cylinder body sleeve 11 along the axial direction and used for cooling and lubricating the main shaft 6 and the cylinder body sleeve 11 through cooling liquid.
As shown in fig. 13 to 14, the piston 2 has a spherical top surface, two angled side surfaces and a piston pin seat at the lower part of the two side surfaces, a piston shaft is protruded at the center of the spherical top surface of the piston 2, and the axis of the piston shaft passes through the center of the spherical top surface of the piston; the piston shaft is inserted into a piston shaft hole 104 on the inner spherical surface of the cylinder cover 1, and the spherical top surface of the piston and the spherical inner cavity have the same spherical center and form sealing movable fit; the piston pin seat is of a semi-cylindrical structure, and a through piston pin hole is formed in the central axis of the semi-cylinder; a piston pin seat at the lower part of the piston 2 is provided with an open gear, a semi-cylindrical groove is formed, the open gear of the piston 2 is positioned in the middle of the piston pin seat and is perpendicular to the axis of a piston pin hole of the piston pin seat, and the open gear width of the piston 2 is matched with the width of a protruding semi-cylinder of the turntable pin seat; in actual production, the piston 2 is formed by coating a PEEK layer, namely a piston PEEK coating 202, on a stainless steel metal matrix, namely a piston matrix 201 in an injection molding mode, so that PEEK coatings are arranged on the surfaces of the piston spherical surface, the outer cylindrical surface and the two side spherical surfaces of a piston pin seat, the two side surfaces and the circular arc bottom surface of a semi-cylindrical groove of the piston pin seat and the cylindrical surface of a piston shaft, and therefore a steel and PEEK friction pair is formed on a moving part, and PEEK material is good in wear resistance, high in strength, corrosion resistance and self-lubricating performance, and has good friction pairing performance with stainless steel.
As shown in fig. 15 to 18, the rotary disk 4 has a rotary disk pin holder corresponding to the piston pin holder at an upper portion thereof; a turntable shaft is protruded from the center of the lower end of the turntable 4, the turntable shaft passes through the spherical center of the sphere of the turntable, and a sliding shoe 403 is arranged at the end part of the turntable shaft; the outer peripheral surface between the upper part and the lower end surface of the turntable 4 is a turntable spherical surface, and the turntable spherical surface and the spherical cavity have the same spherical center and are tightly clung to the spherical cavity to form sealing movable fit; the two ends of the turntable pin boss are semi-cylindrical grooves, the middle part of the turntable pin boss is a convex semi-cylinder, and a through turntable pin hole is formed in the center of the semi-cylinder; the center pin 3 is inserted into a pin hole formed by matching the turntable pin seat and the piston pin seat to form a cylindrical surface hinge, sealing movable fit is formed between each matching surface of the cylindrical surface hinge, and sealing movable fit is formed between two ends of the cylindrical surface hinge and the spherical inner cavity; the piston 3 and the turntable 5 are in sealing dynamic connection through a cylindrical hinge, arc inserts made of PEEK materials are arranged at two ends of the center pin 3, and the shape of the arc is matched with that of the spherical inner cavity. In actual production, the turntable 4 is formed by coating a PEEK layer, namely a turntable PEEK coating 402, on a stainless steel metal substrate, namely a turntable substrate 401 in an injection molding mode, so that PEEK is ensured as surface coatings on two parallel side surfaces of the turntable spherical surface, the sliding shoes 403 and the sliding grooves 601, and a steel and PEEK friction pair is formed on a moving part. The two ends of the center pin 3 are arc surfaces, the cylindrical surface material of the matched part of the center pin 3 and the pin seat of the piston pin seat and the pin hole of the turntable is PEEK, and in order to ensure the strength of the center pin 3, the center pin 3 is coated with a layer of PEEK material on a steel substrate.
As shown in fig. 8 to 12, a main shaft bracket 7 is fixed at the lower end of a cylinder body 5 through a screw, a main shaft 6 is connected at the lower end of the cylinder body 5 through the main shaft bracket 7, a rectangular sliding groove 601 is arranged on the upper end surface of the main shaft 6, the section size of the sliding groove 601 is matched with the thickness size between two parallel side surfaces of a sliding shoe 403 on a rotary table 4, the rotary table shaft extends out of the lower end of the cylinder body 5, the sliding shoe 403 is inserted into the sliding groove 601 at the upper end of the main shaft 6, and the two parallel side surfaces of the sliding shoe 403 are attached to the two side surfaces of the sliding groove 601 to form sliding fit; a bearing 8 and a sealing ring 9 are arranged at the lower end of the main shaft 6 and matched with the main shaft bracket 7; a main shaft bracket reflux groove 701 is arranged on the hole wall of the shaft hole of the main shaft bracket 7, the main shaft bracket reflux groove 701 is communicated with the cylinder body reflux channel 502 on the lower end surface of the cylinder body 5, a main shaft overflow hole 602 is arranged on the bottom surface of the chute 601, the main shaft overflow hole 602 is used for introducing liquid at the upper end of the main shaft 6 into a gap (more than a sealing ring 9) at the matching part of the shaft neck of the lower end of the main shaft 6 and the main shaft bracket 7, and then the liquid flows back into the cylinder body reflux channel 502 from the main shaft bracket reflux groove 701; the main shaft bracket 7 provides support for the rotation of the main shaft, and the lower end of the main shaft 6 is connected with the power mechanism to provide power for the operation of the spherical pump.
The cylinder cover 1 is provided with a cylinder cover diversion channel 103 and a cylinder cover backflow channel 107, the cylinder body 5 is provided with a cylinder body diversion channel 501 and a cylinder body backflow channel 502, the upper ends of the cylinder cover diversion channel 103 and the cylinder cover backflow channel 107 are respectively communicated with the liquid inlet 101, the lower ends of the cylinder cover diversion channel 103 and the cylinder cover backflow channel 107 are arranged on the flange surface of the lower end of the cylinder cover 1, the upper ends of the cylinder body diversion channel 501 and the cylinder body backflow channel 502 are arranged on the flange surface of the upper end of the cylinder body 5, the lower end of the cylinder cover diversion channel 103 is communicated with the upper end of the cylinder body diversion channel 501, the upper end of the cylinder body backflow channel 502 is communicated with the lower end of the cylinder cover backflow channel 107, and the lower end of the cylinder body backflow channel 502 is communicated with the main shaft bracket backflow groove 701; a throttling step is arranged in the liquid inlet hole 101, liquid in the liquid inlet hole 101 is throttled by a throttling surface and then mainly enters a liquid suction working chamber 1001, and a small part of the liquid enters a cooling channel to cool the system; the cylinder cover diversion channel 103, the cylinder body diversion channel 501, the liquid collecting pool, the main shaft bracket backflow groove 701, the cylinder body backflow channel 502 and the cylinder cover backflow channel 107 are sequentially communicated to form a spherical pump cooling channel; the inlet of the cooling channel is communicated with the liquid inlet 101, and the cooling liquid which is shunted from the liquid inlet 101 sequentially enters the cavity formed by the lower end of the cylinder 5, the upper end of the main shaft 6 and the upper end of the main shaft bracket 7 through the cylinder cover shunting channel 103 and the cylinder body shunting channel 501 to form a liquid collecting pool, and then sequentially flows back into the liquid inlet 101 through the main shaft bracket reflux groove 701, the cylinder body reflux channel 502 and the cylinder cover reflux channel 107 to be sucked into the working chamber 1001, so that a cooling circulation system of the spherical pump is formed.
The axes of the piston shaft hole 104 and the turntable shaft pass through the sphere center of the spherical inner cavity, and the included angles between the axes of the piston shaft hole 104 and the turntable shaft and the axis of the main shaft 6 are alpha; the two parallel sides of the sliding shoe 403 are symmetrically arranged at two sides of the axis of the turntable and are parallel to the axis of the cylindrical hinge; when the spindle 6 rotates to drive the rotary table 4 and the piston 2, the sliding shoe 403 slides back and forth in the chute 601, the piston 2 and the rotary table 4 swing relatively, two working chambers 1001 with alternately changed volumes are formed among the upper end surface of the rotary table 4, the two side surfaces of the piston 2 and the spherical inner cavity, and when one working chamber 1001 absorbs liquid, the other working chamber 1001 compresses and discharges liquid; the main shaft 6 rotates once, the piston 2 rotates once around the axis of the piston shaft hole 104, the piston 2 swings once around the axis of the center pin 3 relative to the rotary table 4, meanwhile, the sliding shoe 403 of the rotary table 4 swings once in the sliding groove 601 in the main shaft 6, the swinging swing amplitude is 2α, and the two working chambers 1001 generate a complete liquid suction or compression liquid discharge process respectively.
As shown in fig. 2, 3, 15 to 18, a hydrostatic support is provided between the two parallel sides of the shoe 403 of the turntable 4 and the runner 601, the hydrostatic support including a first fluid flow channel 404, a second fluid flow channel 405 provided on the turntable 4, and fluid bearing grooves provided on the two parallel sides of the shoe 403, the fluid bearing grooves including a first fluid bearing groove 406 and a second fluid bearing groove 407 provided on the two parallel sides of the shoe 403.
A first flow channel 404 and a second flow channel 405 are provided in the turntable 4, the first flow channel 404 comprising a first flow channel inlet 4041, a first channel and a first flow channel outlet 4042; the first fluid channel inlet 4041 is arranged on the upper end surface of the turntable 4 and communicated with one working chamber 1001, the first fluid channel outlet 4042 is arranged on one of two parallel side surfaces of the sliding shoe 403, and the first fluid channel inlet 4041 and the first fluid channel outlet 4042 are respectively arranged on two sides of a plane parallel to the two parallel side surfaces of the sliding shoe 403 (the plane is parallel to the two parallel side surfaces of the sliding shoe 403 and passes through the spherical center of the spherical surface of the turntable) where the axis of the turntable is positioned; the second flow channel 405 includes a second flow channel inlet 4051, a second channel, and a second flow channel outlet 4052; the second fluid channel inlet 4051 is arranged on the upper end surface of the turntable 4 and is communicated with the other working chamber 1001, the second fluid channel outlet 4052 is arranged on the other side surface of the two parallel side surfaces of the sliding shoe 403, and the second fluid channel inlet 4051 and the second fluid channel outlet 5052 are respectively arranged on two sides of a plane (which is parallel to the two parallel side surfaces of the sliding shoe 403 and passes through the spherical center of the spherical surface of the turntable) of the two parallel side surfaces of the sliding shoe 403, where the axis of the turntable is located; the first channel and the second channel are physically independent of each other within the turntable 4. In order to facilitate processing and reduce friction between the sliding shoe 403 and the runner 601, a sliding shoe lining plate 10 is arranged between two parallel sides of the sliding shoe 403 and the side of the runner 601; the runner lining plate 10 is PEEK plate-shaped, the runner lining plate 10 is two, and is respectively arranged on two sides of the parallel side surfaces of the sliding shoe 403, one side of the runner lining plate 10 is attached to the side surface of the runner 601, and the other side is attached to one side of the parallel side surface of the sliding shoe 403; the runner lining board 10 can be integrally processed after being fixed with the runner 601, and during processing, the two side surfaces of the runner lining board 10 are guaranteed to be attached to the two side surfaces of the sliding shoe 403, gaps are controlled, and the two parallel side surfaces of the sliding shoe 403 are attached to the sliding shoe lining boards 10 on the two sides and slide back and forth along the surface of the sliding shoe lining board 10 in the runner 601.
A first liquid bearing groove 406 and a second liquid bearing groove 407 are respectively arranged on two parallel side surfaces of the sliding shoe 403, a first liquid flow channel outlet 4042 is communicated with the first liquid bearing groove 406, and a second liquid flow channel outlet 4052 is communicated with the second liquid bearing groove 407; by minimizing the flow area of the first fluid flow channel outlet 4042 and the second fluid flow channel outlet 4052, the flow rate of the fluid supported by static pressure is controlled, the drop of the apparent efficiency of the volume is avoided, the cross-sectional dimension of the first fluid pressure-bearing groove 406 is far greater than the cross-sectional dimension of the first fluid flow channel outlet 4042, the cross-sectional dimension of the second fluid pressure-bearing groove 407 is far greater than the cross-sectional dimension of the second fluid flow channel outlet 4052, and the surfaces of the first fluid pressure-bearing groove 406 and the second fluid pressure-bearing groove 407 are slightly lower than the planes on both sides of the slipper 403, typically lower than 1 millimeter. The diameters of the first fluid flow channel outlet 4042 and the second fluid flow channel outlet 4052 are generally selected to be 0.3 to 3 mm, and the cross-sectional areas of the first fluid pressure-receiving groove 406 and the second fluid pressure-receiving groove 407 are as large as possible, at least 10 times or more, in order to increase the fluid supporting force of the hydraulic support.
When the spherical pump works, when the working chamber 1001 communicated with the first liquid flow channel 404 is at high pressure, the whole rotor is extruded unidirectionally towards one side (the side where the low-pressure working chamber 1001 is positioned) of the sliding shoe 403, so that the gap between the sliding shoe lining plate 10 and the sliding shoe lining plate 601 matched with the side surface of the sliding shoe 403 provided with the first liquid pressure groove 406 is reduced, and meanwhile, the gap between the spherical surface of the turntable and the spherical cavity at the side where the first liquid pressure groove 406 is arranged is correspondingly reduced, the friction force between the side surface of the sliding shoe provided with the first liquid pressure groove 406 and the sliding shoe lining plate 10 is increased, and the friction force between the spherical surface of the turntable and the spherical cavity is increased; however, since the high-pressure liquid in the first liquid flow channel 404 enters the first liquid pressure groove 406, a larger hydraulic pressure is generated in the first liquid pressure groove 406, and the hydraulic pressure acts between the side surface of the sliding shoe 403 and the sliding shoe lining plate 10 as a static pressure support, so that the unidirectional extrusion of the rotor caused by the high pressure of the working chamber communicated with the first liquid flow channel 404 is balanced, the gap between the side surface of the sliding shoe 403 provided with the first liquid pressure groove 406 and the matched sliding shoe lining plate 10 is increased to a designed value, and the gap between the spherical surface of the turntable and the spherical cavity also tends to be normal, thereby reducing the friction force between the matched surfaces during the operation of the spherical pump, reducing the power consumption of the spherical pump and prolonging the normal service working time of the spherical pump.
Similarly, when the working chamber 1001 connected to the second fluid passage 405 is at high pressure, the whole rotor is pressed in one direction toward the side of the shoe 403 where the second fluid bearing groove 407 is provided (the side of the working chamber 1001 at low pressure), so that the gap between the side of the shoe 403 where the second fluid bearing groove 407 is provided and the shoe lining plate 10 in the matched runner 601 becomes smaller, and at the same time, the gap between the spherical surface of the turntable and the spherical cavity on the side where the second fluid bearing groove 407 is provided becomes smaller, the friction between the side of the shoe where the second fluid bearing groove 407 is provided and the shoe lining plate 10 increases, and the friction between the spherical surface of the turntable and the spherical cavity increases; however, since the high-pressure liquid in the second liquid flow channel 405 enters the second liquid pressure-bearing groove 407, a larger hydraulic pressure is generated in the second liquid pressure-bearing groove 407, and the hydraulic pressure acts between the side surface of the sliding shoe 403 and the sliding shoe lining plate 10 as a static pressure support, so that the unidirectional extrusion force on the rotor caused by the high pressure of the working chamber communicated with the second liquid flow channel 405 is balanced, the gap between the side surface of the sliding shoe 403 provided with the second liquid pressure-bearing groove 407 and the matched sliding shoe lining plate 10 is increased and restored to a designed value, and the gap between the spherical surface of the turntable and the spherical inner cavity also tends to be normal;
the spherical pump is operated periodically, the two working chambers 1001 alternately generate high pressure, the first liquid flow channel 404 and the second liquid flow channel 405 are alternately communicated with the working chambers 1001 with high pressure, unbalance force generated during operation of the rotor is balanced continuously, and gaps between working surfaces are adjusted, so that friction force between the matching surfaces during operation of the spherical pump is reduced, power consumption of the spherical pump is reduced, and normal service working time of the spherical pump is prolonged.
In this patent, the shape of the liquid bearing groove may be rectangular, circular or other shape, and is disposed at the center of each of the two parallel sides of the slipper 403; the liquid pressure-bearing groove can also be designed into a multi-stage pressure-bearing groove, namely a multi-stage liquid pressure-bearing groove, and the multi-stage liquid pressure-bearing groove can also be a multi-stage circular groove or a multi-stage rectangular groove; the multistage pressure-bearing groove comprises a first multistage pressure-bearing groove and a second multistage pressure-bearing groove which are arranged in the center of two parallel side surfaces of the sliding shoe 403, the first liquid flow channel outlet 4042 is communicated with the first multistage pressure-bearing groove, the second liquid flow channel outlet 4052 is communicated with the second multistage pressure-bearing groove, the cross-sectional size of the first multistage pressure-bearing groove is larger than that of the first liquid flow channel outlet 4042, the cross-sectional size of the second multistage pressure-bearing groove is larger than that of the second liquid flow channel outlet 4052, and the surfaces of the first multistage pressure-bearing groove and the second multistage pressure-bearing groove are slightly lower than the planes of two sides of the sliding shoe 403; the first multistage pressure-bearing groove and the second multistage pressure-bearing groove comprise a basic pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves, the basic pressure-bearing groove is arranged in the center of two parallel side surfaces of the sliding shoe 403, the first liquid flow channel outlet 4042 is arranged at the bottom of the basic pressure-bearing groove, so that the first liquid flow channel 404 is communicated with the first multistage pressure-bearing groove, and the second liquid flow channel outlet 4052 is arranged at the bottom of the basic pressure-bearing groove, so that the second liquid flow channel 405 is communicated with the second multistage pressure-bearing groove; the periphery of the basic pressure-bearing groove is respectively provided with a plurality of auxiliary pressure-bearing grooves, and the plurality of auxiliary pressure-bearing grooves sequentially encircle the periphery of the basic pressure-bearing groove; the high-pressure liquid in the basic pressure-bearing groove bears main hydraulic pressure, the high-pressure liquid in the basic pressure-bearing groove overflows and leaks into the peripheral adjacent auxiliary pressure-bearing groove through the clearance part between the side plane of the sliding shoe 403 and the plane of the sliding shoe lining plate 10, the high-pressure liquid in the auxiliary pressure-bearing groove plays a role in static pressure support on the sliding shoe 403, the supporting area is increased, the liquid in the auxiliary pressure-bearing groove overflows and leaks into the peripheral adjacent auxiliary pressure-bearing groove partially, the liquid sequentially leaks to each stage of auxiliary pressure-bearing grooves from the basic pressure-bearing groove, the pressure of the liquid in the multistage pressure-bearing groove is gradually reduced, and the liquid amount is gradually reduced; the multistage pressure-bearing groove has the advantages that the pressure of the basic pressure-bearing groove positioned in the center of the ring can be ensured to be maximum, the liquid flow introduced from the high-pressure working chamber is effectively utilized, the hydrostatic pressure supporting force is stable and distributed uniformly, and the hydrostatic pressure supporting effect is better.
As shown in fig. 19 to 20, the first multistage pressure-bearing groove and the second multistage pressure-bearing groove are rectangular grooves, that is, the first multistage pressure-bearing groove is a first multistage rectangular groove 408, the second multistage pressure-bearing groove is a second multistage rectangular groove 409, the first multistage rectangular groove 408 and the second multistage rectangular groove 409 are respectively arranged on two parallel sides of the slipper 403, the first fluid channel outlet 4042 is arranged at the bottom of the basic pressure-bearing groove of the first multistage rectangular groove 408, so that the first multistage rectangular groove 408 is communicated with the first fluid channel 404, the second fluid channel outlet 4052 is arranged at the bottom of the basic pressure-bearing groove of the second multistage rectangular groove 409, so that the second multistage rectangular groove 409 is communicated with the second fluid channel 405.
As shown in fig. 20 to 21, the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove are circular grooves, that is, the first multi-stage pressure-bearing groove is a first multi-stage circular groove 410, the second multi-stage pressure-bearing groove is a second multi-stage circular groove 411, the first multi-stage circular groove 410 and the second multi-stage circular groove 410 are respectively arranged on two parallel sides of the slipper 403, the first fluid channel outlet 4042 is arranged at the bottom of the basic pressure-bearing groove of the first multi-stage circular groove 410, so that the first multi-stage circular groove 410 is communicated with the first fluid channel 404, and the second fluid channel outlet 4052 is arranged at the bottom of the basic pressure-bearing groove of the second multi-stage circular groove 411, so that the second multi-stage circular groove 410 is communicated with the second fluid channel 405.
In order to simplify the processing technology, when the first liquid flow channel 404 and the second liquid flow channel 405 are processed, the first liquid flow channel 404 can be formed by combining a plurality of sections of straight channels, when the first liquid flow channel 404 is processed, holes are drilled downwards from the position of a first liquid flow channel inlet 4041 positioned on the upper end surface of the turntable 4 at a certain angle, holes are drilled upwards from the lower end part of the sliding shoe 403 at a certain angle and communicated with the holes, then a first liquid flow channel outlet hole 4042 is drilled and milled from the bottom of a liquid pressure-bearing groove on the side surface of the sliding shoe 403 and communicated with the holes, and finally the hole opening of the lower end part of the sliding shoe 403 is plugged; the second flow channel 405 is processed by the same method, firstly, a hole is drilled downwards at a certain angle from the position of a second flow channel inlet 4051 positioned on the upper end surface of the turntable 4, then a hole is drilled upwards at a certain angle from the lower end part of the sliding shoe 403 and communicated with the hole, then a second flow channel outlet hole 4052 is drilled and milled from the bottom of a liquid pressure-bearing groove on the side surface of the sliding shoe 403 and communicated with the hole, and finally, the hole at the lower end part of the sliding shoe 403 is plugged.
Claims (5)
1. A hydrostatic support for a spherical pump rotor is characterized in that: the hydraulic control device comprises a first liquid flow channel (404), a second liquid flow channel (405) and liquid pressure-bearing grooves, wherein the first liquid flow channel (404) and the second liquid flow channel (405) are arranged on a turntable (4), the liquid pressure-bearing grooves are arranged on two parallel sides of a sliding shoe (403), a first liquid flow channel inlet (4041) is communicated with one working chamber (1001), a second liquid flow channel inlet (4051) is communicated with the other working chamber (1001), and a first liquid flow channel outlet (4042) and a second liquid flow channel outlet (4052) are respectively communicated with the liquid pressure-bearing grooves on two parallel sides of the sliding shoe (403); a slipper liner plate (10) is arranged between the two parallel side surfaces of the slipper (403) and the side surface attached to the chute (601); two parallel side surfaces of the sliding shoe (403) are adhered to the sliding shoe lining plates (10) on two sides and slide back and forth along the surfaces of the sliding shoe lining plates (10) in the sliding groove (601); the hydrostatic support is arranged between two parallel sides of the slipper (403) and the slipper liner (10).
2. A spherical pump rotor hydrostatic support as defined in claim 1, wherein: the first liquid flow channel inlet (4041) is arranged on the upper end surface of the rotary table (4) and communicated with the working chamber (1001), the first liquid flow channel outlet (4042) is arranged on one of two parallel side surfaces of the sliding shoe (403), and the first liquid flow channel inlet (4041) and the first liquid flow channel outlet (4042) are respectively arranged on two sides of a plane parallel to the two parallel side surfaces of the sliding shoe (403) where the axis of the rotary table (4) is positioned; the second liquid flow channel inlet (4051) is arranged on the upper end face of the rotary table (4) and communicated with the other working chamber (1001), the second liquid flow channel outlet (4052) is arranged on the other side face of the two parallel side faces of the sliding shoe (403), and the second liquid flow channel inlet (4051) and the second liquid flow channel outlet (4052) are respectively arranged on two sides of a plane parallel to the two parallel side faces of the sliding shoe (403) where the axis of the rotary table (4) is located.
3. A spherical pump rotor hydrostatic support as defined in claim 1, wherein: the liquid pressure-bearing groove comprises a first liquid pressure-bearing groove (406) and a second liquid pressure-bearing groove (407) which are arranged on two parallel side surfaces of the sliding shoe (403), the first liquid flow channel outlet (4042) is communicated with the first liquid pressure-bearing groove (406), the second liquid flow channel outlet (4052) is communicated with the second liquid pressure-bearing groove (407), the cross-sectional size of the first liquid pressure-bearing groove (406) is larger than that of the first liquid flow channel outlet (4042), the cross-sectional size of the second liquid pressure-bearing groove (407) is larger than that of the second liquid flow channel outlet (4052), and the surfaces of the first liquid pressure-bearing groove (406) and the second liquid pressure-bearing groove (407) are slightly lower than the planes on two sides of the sliding shoe.
4. A spherical pump rotor hydrostatic support as defined in claim 1, wherein: the liquid pressure-bearing groove comprises a first multistage pressure-bearing groove and a second multistage pressure-bearing groove which are arranged on two parallel side surfaces of the sliding shoe (403), the first liquid flow channel outlet (4042) is communicated with the first multistage pressure-bearing groove, the second liquid flow channel outlet (4052) is communicated with the second multistage pressure-bearing groove, the cross-sectional size of the first multistage pressure-bearing groove is larger than that of the first liquid flow channel outlet (4042), the cross-sectional size of the second multistage pressure-bearing groove is larger than that of the second liquid flow channel outlet (4052), and the surfaces of the first multistage pressure-bearing groove and the second multistage pressure-bearing groove are slightly lower than the planes on two sides of the sliding shoe (403); the first multistage pressure-bearing groove and the second multistage pressure-bearing groove both comprise a basic pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves, the basic pressure-bearing groove is arranged in the center of two parallel side surfaces of the sliding shoe (403), the bottom of the basic pressure-bearing groove is communicated with the first liquid flow channel outlet (4042) or the second liquid flow channel outlet (4052), the plurality of auxiliary pressure-bearing grooves are respectively arranged on the periphery of the basic pressure-bearing groove, and the plurality of auxiliary pressure-bearing grooves sequentially encircle the periphery of the basic pressure-bearing groove.
5. A spherical pump rotor hydrostatic support as defined in claim 1, wherein: the liquid pressure-bearing grooves can be round grooves or rectangular grooves, and the multi-stage liquid pressure-bearing grooves can be multi-stage round grooves or multi-stage rectangular grooves.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911060871.1A CN110701040B (en) | 2019-11-01 | 2019-11-01 | Static pressure support for spherical pump rotor |
| EP20882813.7A EP4053411A4 (en) | 2019-11-01 | 2020-10-22 | Spherical pump rotor static pressure support and spherical pump provided with static pressure support |
| KR1020227014536A KR102653700B1 (en) | 2019-11-01 | 2020-10-22 | A spherical pump having a rotor static pressure support structure and a static pressure support structure. |
| JP2022550043A JP7430854B2 (en) | 2019-11-01 | 2020-10-22 | Spherical pump rotor static pressure support structure and spherical pump with static pressure support structure |
| PCT/CN2020/122673 WO2021083019A1 (en) | 2019-11-01 | 2020-10-22 | Spherical pump rotor static pressure support and spherical pump provided with static pressure support |
| US17/728,939 US11802560B2 (en) | 2019-11-01 | 2022-04-25 | Hydrostatic pressure support for spherical pump rotor and spherical pump with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911060871.1A CN110701040B (en) | 2019-11-01 | 2019-11-01 | Static pressure support for spherical pump rotor |
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| CN110701040A CN110701040A (en) | 2020-01-17 |
| CN110701040B true CN110701040B (en) | 2023-12-01 |
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| CN201911060871.1A Active CN110701040B (en) | 2019-11-01 | 2019-11-01 | Static pressure support for spherical pump rotor |
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| JP7430854B2 (en) | 2019-11-01 | 2024-02-14 | 深▲セン▼市球形動力科技有限公司 | Spherical pump rotor static pressure support structure and spherical pump with static pressure support structure |
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Effective date of registration: 20230809 Address after: A706, Block A, TCL Building, No. 6 Gaoxinyuan 1st Road, Yuehai Street, Nanshan District, Shenzhen City, Guangdong Province, 518000 Applicant after: Shenzhen Spherical Power Technology Co.,Ltd. Address before: 518000 Room 201, building A, No. 1, Qian Wan Road, Qianhai Shenzhen Hong Kong cooperation zone, Shenzhen, Guangdong (Shenzhen Qianhai business secretary Co., Ltd.) Applicant before: Shenzhen Zhong'an Power Technology Co.,Ltd. |
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