CN110701040A - Static pressure support for spherical pump rotor - Google Patents
Static pressure support for spherical pump rotor Download PDFInfo
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- CN110701040A CN110701040A CN201911060871.1A CN201911060871A CN110701040A CN 110701040 A CN110701040 A CN 110701040A CN 201911060871 A CN201911060871 A CN 201911060871A CN 110701040 A CN110701040 A CN 110701040A
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- pressure
- bearing groove
- liquid
- sliding shoe
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- 230000003068 static effect Effects 0.000 title claims abstract description 15
- 239000007788 liquid Substances 0.000 claims abstract description 153
- 239000012530 fluid Substances 0.000 claims description 54
- 230000002706 hydrostatic effect Effects 0.000 claims description 9
- 238000000034 method Methods 0.000 abstract description 6
- 239000004696 Poly ether ether ketone Substances 0.000 description 16
- 229920002530 polyetherether ketone Polymers 0.000 description 16
- 238000010992 reflux Methods 0.000 description 10
- 238000007789 sealing Methods 0.000 description 9
- 238000001816 cooling Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 7
- 239000011248 coating agent Substances 0.000 description 6
- 238000000576 coating method Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000008093 supporting effect Effects 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 238000005253 cladding Methods 0.000 description 3
- 230000007246 mechanism 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
- 239000000758 substrate Substances 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 238000001125 extrusion Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
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- 230000002093 peripheral effect Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 229920003023 plastic Polymers 0.000 description 1
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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 for 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 static pressure support comprises a first liquid flow channel (404) arranged on the rotary disc (4), a second liquid flow channel (405) and liquid pressure bearing grooves arranged on two parallel side surfaces of the sliding shoe (403), wherein 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 the two parallel side surfaces of the sliding shoe (403); the advantage of this patent has eliminated the unbalanced force of spherical pump operation in-process, has guaranteed the clearance between the fitting surface, has reduced the consumption of spherical pump.
Description
Technical Field
The patent relates to a volume-variable mechanism, in particular to a static pressure support for a spherical pump rotor.
Background
The ball pump is a new-invented variable-volume mechanism with new structure in recent years, and its advantages are no air intake/exhaust valve, less moving parts, and surface contact between all moving parts to form a surface sealing structure, so that it can implement high pressure and structure miniaturization. Spherical pumps have been used in practice today as a new construction for pump type machines. However, because a fixed included angle is formed between the axis of the piston of the spherical pump and the main shaft, the pressures in the two working chambers change in a reciprocating manner, when one working chamber is at a high pressure, the other working chamber is at a low pressure, so that the piston and the rotary table deflect to one side of the low pressure to extrude the spherical surface of the cylinder body, a gap between the rotary table and the spherical surface of the cylinder body on the side is reduced, an oil film or a water film is damaged, the friction force is increased, and accordingly, the power consumption is increased, and the rotor and the sliding shoe are abnormally abraded.
Disclosure of Invention
The invention aims to design a static pressure support for a spherical pump rotor, which is added on a sliding shoe of the spherical pump rotor, balances unbalanced force in the operation process of the spherical pump through liquid pressure generated by the spherical pump, reduces operation power consumption and prolongs the service life of the spherical pump.
The invention has the technical scheme that the spherical pump rotor static pressure support is characterized in that: the static pressure support comprises a first liquid flow channel, a second liquid flow channel and liquid pressure bearing grooves, the first liquid flow channel and the second liquid flow channel are arranged on the rotary disc, the liquid pressure bearing grooves are arranged on two parallel side surfaces of the sliding shoe, an inlet of the first liquid flow channel is communicated with one working chamber, an inlet of the second liquid flow channel is communicated with the other working chamber, and an outlet of the first liquid flow channel and an 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 chute; two parallel side surfaces of the sliding shoes are attached to the sliding shoe lining plates on the two sides and slide in the sliding grooves along the surfaces of the sliding shoe lining plates in a reciprocating mode; the static pressure support is arranged between two parallel side surfaces of the sliding shoe and the sliding shoe lining plate;
the inlet of the first liquid flow channel is arranged on the upper end surface of the rotary disc and communicated with a working chamber, the outlet of the first liquid flow channel is arranged on one of the two parallel side surfaces of the skid shoe, and the inlet of the first liquid flow channel and the outlet of the first liquid flow channel are respectively positioned on two sides of a plane where the axis of the rotary disc is positioned and which is parallel to the two parallel side surfaces of the skid shoe; the inlet of the second liquid flow channel is arranged on the upper end surface of the rotary disc and communicated with the other working chamber, the outlet of the second liquid flow channel is arranged on the other side surface of the two parallel side surfaces of the sliding shoe, and the inlet of the second liquid flow channel and the outlet of the second liquid flow channel are respectively positioned on two sides of a plane where the axis of the rotary disc is positioned and which is parallel to the two parallel side surfaces of the sliding shoe;
the liquid bearing grooves comprise a first liquid bearing groove and a second liquid bearing groove which are arranged on two parallel side surfaces of the sliding shoe, an outlet of a first liquid flow channel is communicated with the first liquid bearing groove, an outlet of a second liquid flow channel is communicated with the second liquid bearing groove, the cross section size of the first liquid bearing groove is larger than that of the outlet of the first liquid flow channel, the cross section size of the second liquid bearing groove is larger than that of the outlet of the second liquid flow channel, and the surfaces of the first liquid bearing groove and the second liquid bearing groove are slightly lower than the planes of two sides of the sliding shoe;
the liquid bearing grooves comprise a first multistage bearing groove and a second multistage bearing groove which are arranged on two parallel side surfaces of the sliding shoe, an outlet of a first liquid flow channel is communicated with the first multistage bearing groove, an outlet of a second liquid flow channel is communicated with the second multistage bearing groove, the cross section size of the first multistage bearing groove is larger than that of the outlet of the first liquid flow channel, the cross section 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 of two sides of the sliding shoe; the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove respectively comprise a basic pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves, the basic pressure-bearing grooves are arranged in the centers of two parallel side surfaces of the sliding shoe, the bottom of the basic pressure-bearing groove is communicated with the outlet of the first liquid flow channel or the outlet of the second liquid flow channel, 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 are sequentially encircled on the periphery of the basic pressure-bearing groove;
the liquid pressure bearing groove can be a circular groove or a rectangular groove, and the multistage liquid pressure bearing groove can be a multistage circular groove or a multistage rectangular groove;
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 is arranged on the sliding shoes to support smaller force, and larger balanced force can be obtained on the turntable due to the lever action; the uniform clearance among the spherical surface of the piston, the spherical surface of the turntable and the spherical inner cavity is ensured, and the friction loss and the friction force are reduced; meanwhile, the friction force between the sliding shoes and the sliding grooves is reduced; the unbalance force in the running process of the spherical pump is eliminated, the gap between 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; can be used for an oil pump and a water pump.
Drawings
FIG. 1: the structure schematic diagram of the spherical pump;
FIG. 2: FIG. 1 is a sectional view taken along line A-A;
FIG. 3: FIG. 1 is a sectional view taken along line B-B;
FIG. 4: the structure schematic diagram of the cylinder cover;
FIG. 5: FIG. 4 is a cross-sectional view taken along line C-C;
FIG. 6: a schematic structural diagram of the cylinder body;
FIG. 7: FIG. 6 is a cross-sectional view taken along line D-D;
FIG. 8: a schematic structural diagram of the main shaft;
FIG. 9: section E-E in FIG. 8;
FIG. 10: a schematic structural diagram of a main shaft bracket;
FIG. 11: FIG. 10 is a sectional view taken along line H-H;
FIG. 12: FIG. 10 is a sectional view taken along line F-F;
FIG. 13: the piston structure is schematic;
FIG. 14: FIG. 13 is a sectional view taken along line L-L;
FIG. 15: a schematic view of a turntable structure;
FIG. 16: FIG. 15 is a cross-sectional view taken along line K-K;
FIG. 17: a turntable structure perspective view;
FIG. 18: a perspective view of the piston structure;
FIG. 19: the multistage liquid bearing groove is a schematic structural diagram of a sliding shoe of a rectangular bearing groove;
FIG. 20: FIG. 19 is a cross-sectional view taken along line M-M;
FIG. 21: the multistage liquid bearing groove is a schematic structural diagram of a sliding shoe of a circular bearing groove;
FIG. 22: FIG. 21 is a view taken in section N-N;
in the figure: 1-a cylinder cover; 2-a piston; 3-a center pin; 4-a turntable; 5-cylinder body; 6-a main shaft; 7-a spindle support; 8-a bearing; 9-a sealing ring; 10-sliding shoe lining board; 11-cylinder body sleeve;
101-liquid inlet hole; 102-drain holes; 103-cylinder cover shunting channel; 104-piston shaft hole; 105-liquid inlet waist-shaped holes; 106-liquid discharge waist-shaped holes; 107-cylinder cover return passage; 108-chip space;
201-piston base body; 202-piston PEEK coating;
401 — a turntable base; 402-turntable PEEK coating; 403-a slipper; 404-a first flow channel; 4041-first flow channel inlet; 4042-a first flow channel outlet; 405-a second flow channel; 4051-a second flow channel inlet; 4052-a second flow channel outlet; 406-a first fluid pressure bearing groove; 407-a second fluid pressure bearing tank; 408-a first multilevel rectangular slot; 409-a second multilevel rectangular slot; 410-a first multi-stage circular groove; 411-a second multi-level circular slot;
501-cylinder body shunting channel; 502-cylinder return channel;
601-a chute; 602-a main shaft overflowing hole; 701-a main shaft support reflux groove; 1001 — working chamber.
Detailed Description
As shown in fig. 1 to 3, the spherical pump described in this patent includes a cylinder cover 1, a piston 2, a turntable 4, a cylinder body 5, a main shaft 6, a main shaft bracket 7, etc., the cylinder body 5 and the cylinder cover 1 have a hemispherical inner cavity, and the cylinder body 5, the cylinder cover 1 and the main shaft bracket 7 are fixedly connected by screws in sequence to form a spherical pump casing with a spherical inner cavity, i.e., a spherical pump stator; the piston 2, the turntable 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 a central pin 3, the piston shaft is inserted into a 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 provided on the upper end surface of the cylinder head 1, and a liquid inlet waist-shaped hole 105, a liquid outlet waist-shaped hole 106 and a piston shaft hole 104 are provided on the inner spherical surface of the cylinder head 1; the axis of the piston shaft hole 104 passes through the sphere center of the inner spherical surface of the cylinder cover, the orifices of the liquid inlet waist-shaped hole 105 and the liquid discharge waist-shaped hole 106 on the inner spherical surface of the cylinder cover 1 are respectively arranged in an annular space vertical to the axis of the piston shaft hole 104, the liquid inlet waist-shaped hole 105 is communicated with the liquid inlet hole 101 at the upper end of the cylinder cover 1, and the liquid discharge waist-shaped hole 106 is communicated with the liquid discharge hole 102 at the upper end of the. The liquid inlet and outlet control is realized by the rotation of the piston 2, and when each working chamber needs to discharge liquid or feed liquid, the corresponding working chamber is communicated with the liquid inlet waist-shaped hole 105 or the liquid outlet waist-shaped hole 106. In order to prevent the abrasive dust generated when the piston shaft rotates in the piston shaft hole 104 from entering between the piston spherical surface and the inner spherical surface of the cylinder cover 1, a chip discharge groove 108 is arranged on the inner spherical surface of the cylinder cover 1, and one end of the chip discharge groove 108 is communicated with the liquid inlet waist-shaped hole 105; the other end of the chip groove 108 extends along the direction of the inner spherical surface of the cylinder cover towards the piston shaft hole 104 and extends to the position near the orifice of the piston shaft hole 104, the section of the chip groove 108 is U-shaped, the 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; thus, the swarf discharged from the piston shaft bore 104 is collected in the swarf discharge groove 108, and is discharged out of the cylinder with the fluid entering the working chamber 1001.
As shown in fig. 6 and 7, the lower end of the cylinder body 5 is provided with a turntable shaft through hole penetrating through the outside of the cylinder, and the size of the hole is large enough to ensure that the turntable shaft does not interfere with the cylinder body 5 in the rotation process of the turntable 4; the cylinder body sleeve 11 is arranged at the part where the main shaft 6 is matched with the lower end of the cylinder body 5, a cylinder body sleeve hole is arranged at the lower end of the cylinder body 5, the cylinder body sleeve 11 is arranged in the cylinder body sleeve hole and is used for upper end rotary support (equivalent to a sliding bearing) when the main shaft 6 rotates, the axis of the cylinder body sleeve hole and the axis of the cylinder body sleeve 11 are overlapped and pass through the spherical center of the inner spherical surface of the cylinder body, the inner diameter of the cylinder body sleeve 11 is matched with the upper end shaft neck of the main shaft 6, 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 made of PEEK, through cooling grooves are axially arranged on the outer cylinder and the inner cylindrical surface of the cylinder body sleeve 11 and are used for cooling.
As shown in fig. 13 to 14, the piston 2 has a spherical top surface, two angled side surfaces and piston pin bosses at lower portions of the side surfaces, a piston shaft is projected at the center of the spherical top surface of the piston 2, and an axis of the piston shaft passes through a spherical 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; an opening is arranged on a piston pin boss at the lower part of the piston 2 to form a semi-cylindrical groove, the opening of the piston 2 is positioned in the middle of the piston pin boss and is vertical to the axis of a piston pin hole of the piston pin boss, and the opening width of the piston 2 is matched with the width of a convex semi-cylindrical body of the turntable pin boss; in actual production, piston 2 is through the mode cladding one deck PEEK layer that piston PEEK cladding 202 of moulding plastics on stainless steel metal substrate namely piston base 201, guarantee in piston sphere, the outer cylinder face and the both sides sphere of piston pin boss, the both sides face and the circular arc bottom surface of the semi-cylindrical recess of piston pin boss, the surface of piston axle cylinder face set up the PEEK cladding to make the motion part form steel and PEEK friction pair, the PEEK material is wear-resisting, intensity is high, corrosion-resistant and self-lubricating property, be good wear-resisting material, and have good friction pairing performance with the stainless steel.
As shown in fig. 15 to 18, the rotary plate 4 has a rotary plate pin boss corresponding to the piston pin boss at an upper portion thereof; a turntable shaft protrudes from the center of the lower end of the turntable 4, passes through the spherical center of the spherical surface of the turntable, and a sliding shoe 403 is arranged at the end part of the turntable shaft; the 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 inner cavity have the same spherical center and are tightly attached to the spherical inner cavity to form sealing movable fit; the two ends of the turntable pin seat are semi-cylindrical grooves, the middle part of the turntable pin seat is a raised 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 base and the piston pin base to form a cylindrical surface hinge, the matching surfaces of the cylindrical surface hinge form a sealing movable fit, and the two ends of the cylindrical surface hinge and the spherical inner cavity form a sealing movable fit; the piston 3 and the turntable 5 form sealing movable 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 practical production, the turntable 4 is formed by coating a layer of PEEK (polyetheretherketone) coating 402 on a stainless steel metal substrate, namely a turntable substrate 401, in an injection molding manner, and the PEEK coating is ensured on the spherical surface of the turntable and the surfaces of two parallel side surfaces, which are attached to the sliding groove 601, of the sliding shoe 403, so that a steel and PEEK friction pair is formed at a moving part. The two ends of the center pin 3 are arc surfaces, the cylindrical surface material of the part of the center pin 3 matched with the piston pin base and the pin hole of the turntable pin base is PEEK, and in order to ensure the strength of the center pin 3, the center pin 3 is formed by coating a layer of PEEK material on a steel matrix.
As shown in fig. 8 to 12, the main shaft bracket 7 is fixed at the lower end of the cylinder 5 by screws, the main shaft 6 is connected at the lower end of the cylinder 5 by the main shaft bracket 7, a rectangular chute 601 is arranged on the upper end surface of the main shaft 6, the cross-sectional dimension of the chute 601 is matched with the thickness dimension between two parallel side surfaces of the slipper 403 on the turntable 4, the slipper 403 is inserted into the chute 601 at the upper end of the main shaft 6 after the turntable shaft extends out of the lower end of the cylinder 5, and two parallel side surfaces of the slipper 403 are attached to two side surfaces of the chute 601 to form sliding fit; a bearing 8 and a sealing ring 9 are arranged at the part of the lower end of the main shaft 6 matched with the main shaft bracket 7; a main shaft support reflux groove 701 is arranged on the hole wall of the shaft hole of the main shaft support 7, the main shaft support reflux groove 701 is communicated with a cylinder body reflux channel 502 on the lower end surface of a cylinder body 5, a main shaft overflowing hole 602 is arranged on the bottom surface of the sliding groove 601, and the main shaft overflowing hole 602 is used for introducing liquid at the upper end of a main shaft 6 into a gap (above a sealing ring 9) between a lower end journal of the main shaft 6 and a matching part of the main shaft support 7 and then refluxing the liquid into the cylinder body reflux channel 502 from the main shaft support reflux groove; the main shaft support 7 provides support for the rotation of the main shaft, and the lower end of the main shaft 6 is connected with a power mechanism to provide power for the running of the spherical pump.
A cylinder cover shunting channel 103 and a cylinder cover backflow channel 107 are arranged on a cylinder cover 1, a cylinder body shunting channel 501 and a cylinder body backflow channel 502 are arranged on a cylinder body 5, the upper end of the cylinder cover shunting channel 103 and the upper end of the cylinder cover backflow channel 107 are respectively communicated with a liquid inlet hole 101, the lower ends of the cylinder cover shunting channel 103 and the cylinder cover backflow channel 107 are arranged on a flange surface at the lower end of the cylinder cover 1, the upper ends of the cylinder body shunting channel 501 and the cylinder body backflow channel 502 are arranged on a flange surface at the upper end of the cylinder body 5, the lower end of the cylinder cover shunting channel 103 is communicated with the upper end of the cylinder body shunting 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; 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 mainly enters a liquid suction working chamber 1001, and a small part of liquid enters a cooling channel to cool the system; the cylinder cover flow distribution channel 103, the cylinder body flow distribution channel 501, the liquid collecting tank, the main shaft support 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, the cooling liquid which is shunted from the liquid inlet 101 enters cavities 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 support 7 through the cylinder cover shunt channel 103 and the cylinder body shunt channel 501 in sequence to form a liquid collecting tank, and then flows back into the liquid inlet 101 through the main shaft support reflux groove 701, the cylinder body reflux channel 502 and the cylinder cover reflux channel 107 in sequence and is 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 spherical 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 both alpha; the two parallel side surfaces of the sliding shoes 403 are symmetrically arranged on the two sides of the axis of the turntable and are parallel to the axis of the cylindrical surface hinge; when the main shaft 6 drives the rotary table 4 and the piston 2 to rotate, the sliding shoe 403 slides in the sliding groove 601 in a reciprocating manner, the piston 2 and the rotary table 4 swing relatively, two working chambers 1001 with the volume changing alternately are formed among the upper end face of the rotary table 4, two side faces 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 for a circle, the piston 2 rotates for a circle 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 swing amplitude of the swing is 2 alpha, and the two working chambers 1001 respectively perform a complete liquid suction or compression liquid discharge process.
As shown in fig. 2, 3, and 15 to 18, a hydrostatic support is provided between both parallel side surfaces of the slipper 403 of the rotary disk 4 and the slide groove 601, and includes a first fluid passage 404, a second fluid passage 405 provided on the rotary disk 4, and fluid pressure receiving grooves including a first fluid pressure receiving groove 406 and a second fluid pressure receiving groove 407 provided on both parallel side surfaces of the slipper 403.
A first flow channel 404 and a second flow channel 405 are arranged in the rotating disk 4, the first flow channel 404 comprises a first flow channel inlet 4041, a first channel and a first flow channel outlet 4042; the first liquid flow channel inlet 4041 is arranged on the upper end face of the rotary disk 4 and communicated with one working chamber 1001, the first liquid flow channel outlet 4042 is arranged on one of the two parallel side faces 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 (the plane is parallel to the two parallel side faces of the sliding shoe 403 and passes through the spherical center of the spherical surface of the rotary disk) which is parallel to the axis of the rotary disk and is parallel to the two parallel side faces of the sliding shoe 403; the second flow path 405 includes a second flow path inlet 4051, a second path, and a second flow path outlet 4052; a second fluid passage inlet 4051 is provided on the upper end face of the rotary disk 4 and communicates with the other working chamber 1001, a second fluid passage outlet 4052 is provided on the other of the two parallel side faces of the slipper 403, and the second fluid passage inlet 4051 and the second fluid passage outlet 5052 are respectively located on both sides of a plane (which is parallel to the two parallel side faces of the slipper 403 and passes through the spherical center of the spherical surface of the rotary disk) on which the axis of the rotary disk lies and which is parallel to the two parallel side faces of the slipper 403; the first and second channels are physically independent of each other within the carousel 4. In order to facilitate processing and reduce the friction force between the sliding shoes 403 and the sliding grooves 601, sliding shoe lining plates 10 are arranged between two parallel side surfaces of the sliding shoes 403 and the side surfaces of the sliding grooves 601; the sliding chute lining plates 10 are in a PEEK plate shape, two sliding chute lining plates 10 are arranged on two sides of the parallel side faces of the sliding shoes 403 respectively, one side of each sliding chute lining plate 10 is attached to the side face of the sliding chute 601, and the other side of each sliding chute lining plate 10 is attached to one side of the parallel side face of the sliding shoes 403; the chute liner plate 10 can be integrally processed after being fixed with the chute 601, the two side surfaces of the chute liner plate 10 are attached to the two side surfaces of the sliding shoes 403 during processing, the gap is controlled, and the two parallel side surfaces of the sliding shoes 403 are attached to the sliding shoe liner plates 10 on the two sides and slide in the chute 601 along the surfaces of the sliding shoe liner plates 10 in a reciprocating manner.
A first liquid pressure-bearing groove 406 and a second liquid pressure-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 pressure-bearing groove 406, and a second liquid flow channel outlet 4052 is communicated with the second liquid pressure-bearing groove 407; by minimizing the flow area of the first fluid passageway outlet 4042 and the second fluid passageway outlet 4052, thereby controlling the fluid flow rate of the hydrostatic support, a significant decrease in volumetric efficiency is avoided, the cross-sectional dimension of the first fluid pressure-bearing groove 406 is much larger than the cross-sectional dimension of the first fluid passageway outlet 4042, the cross-sectional dimension of the second fluid pressure-bearing groove 407 is much larger than the cross-sectional dimension of the second fluid passageway 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 mm. The diameters of the first flow path outlet 4042 and the second flow path outlet 4052 are generally selected to be 0.3 to 3 mm, and in order to increase the fluid supporting force of the hydraulic support, the cross-sectional areas of the first fluid pressure-bearing groove 406 and the second fluid pressure-bearing groove 407 are as large as possible, at least 10 times larger.
When the spherical pump works, when the working chamber 1001 communicated with the first liquid flow channel 404 is under high pressure, the whole rotor is unidirectionally extruded towards one side (the side where the low-pressure working chamber 1001 is located) of the sliding shoe 403 provided with the first liquid pressure-bearing groove 406, so that the gap between the side surface of the sliding shoe 403 provided with the first liquid pressure-bearing groove 406 and the sliding shoe lining plate 10 in the matched sliding groove 601 is reduced, meanwhile, the gap between the spherical surface of the turntable located at the side provided with the first liquid pressure-bearing groove 406 and the spherical inner cavity is correspondingly reduced, the friction between the side surface of the sliding shoe provided with the first liquid pressure-bearing groove 406 and the sliding shoe lining plate 10 is increased, and the friction between the spherical surface of the turntable and the spherical inner cavity is increased; however, since the high-pressure liquid in the first liquid flow channel 404 enters the first liquid pressure-bearing groove 406 at this time, a large hydraulic pressure is generated in the first liquid pressure-bearing groove 406, and the hydraulic pressure acts between the side surface of the slipper 403 and the slipper lining plate 10 as a static pressure support, so that the unidirectional extrusion on the rotor due to 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 slipper 403 provided with the first liquid pressure-bearing groove 406 and the matched slipper lining plate 10 is increased and restored to a design value, and the gap between the spherical surface of the rotary disc and the spherical inner cavity also tends to be normal, thereby reducing the friction force between the matching surfaces when the spherical pump operates, 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 a high pressure, the entire rotor is unidirectionally pressed toward the side of the shoe 403 (the side of the working chamber 1001 at a low pressure) where the second fluid pressure-bearing groove 407 is formed, so that the gap between the side of the shoe 403 where the second fluid pressure-bearing groove 407 is formed and the shoe lining plate 10 in the sliding groove 601 fitted therewith is reduced, and the gap between the spherical surface of the turntable located on the side where the second fluid pressure-bearing groove 407 is formed and the spherical inner cavity is correspondingly reduced, so that the friction between the shoe side where the second fluid pressure-bearing groove 407 is formed and the shoe lining plate 10 is increased, and the friction between the spherical surface of the turntable and the spherical inner cavity is increased; however, since the high-pressure fluid in the second fluid passage 405 enters the second fluid pressure-bearing groove 407, a large hydraulic pressure is generated in the second fluid pressure-bearing groove 407, and the hydraulic pressure acts as a static pressure support between the side surface of the slipper 403 and the slipper lining plate 10, so that the unidirectional extrusion force on the rotor due to the high pressure of the working chamber communicated with the second fluid passage 405 is balanced, the gap between the side surface of the slipper 403 provided with the second fluid pressure-bearing groove 407 and the matched slipper lining plate 10 is increased and restored to the design value, and the gap between the spherical surface of the turntable and the spherical inner cavity also tends to be normal;
the spherical pump runs periodically, the two working chambers 1001 generate high pressure alternately, the first liquid flow channel 404 and the second liquid flow channel 405 are communicated with the high pressure working chambers 1001 alternately, unbalance force generated when the rotor runs is balanced continuously, and gaps between working surfaces are adjusted, so that friction force between matching surfaces is reduced when the spherical pump runs, 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 fluid pressure-bearing groove may be rectangular, circular or other shapes, and is disposed in 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 grooves comprise a first multistage pressure-bearing groove and a second multistage pressure-bearing groove which are arranged in the centers of two parallel side surfaces of the sliding shoe 403, a first liquid flow channel outlet 4042 is communicated with the first multistage pressure-bearing groove, a 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 and second multistage pressure-bearing grooves each include a basic pressure-bearing groove provided at the center of both parallel sides of the shoe 403 and a plurality of auxiliary pressure-bearing grooves, the first flow path outlet 4042 is provided at the bottom of the basic pressure-bearing groove so that the first flow path 404 is communicated with the first multistage pressure-bearing groove, and the second flow path outlet 4052 is provided at the bottom of the basic pressure-bearing groove so that the second flow path 405 is communicated with the second multistage pressure-bearing groove; a plurality of auxiliary pressure bearing grooves are respectively arranged on the periphery of the basic pressure bearing groove, and the auxiliary pressure bearing grooves are sequentially surrounded on the periphery of the basic pressure bearing groove; high-pressure liquid in the basic pressure-bearing grooves bears main hydraulic pressure, the high-pressure liquid in the basic pressure-bearing grooves partially overflows and leaks into auxiliary pressure-bearing grooves adjacent to the periphery through a plane fit gap between the side plane of the sliding shoe 403 and the plane of the sliding shoe lining plate 10, the sliding shoe 403 is supported by the high-pressure liquid in the auxiliary pressure-bearing grooves in a static pressure manner, the supporting area is increased, the liquid in the auxiliary pressure-bearing grooves partially overflows and leaks into the auxiliary pressure-bearing grooves adjacent to the periphery, the liquid in the auxiliary pressure-bearing grooves sequentially flows outwards to the auxiliary pressure-bearing grooves at each stage, the pressure of the liquid in the multistage pressure-bearing grooves is gradually reduced, and the liquid amount is gradually; 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 guaranteed to be the maximum, the liquid flow introduced from the high-pressure working chamber is effectively utilized, the hydrostatic pressure supporting force is stable and is 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 both 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 disposed on two parallel side surfaces of the sliding shoe 403, a first flow channel outlet 4042 is disposed at the bottom of the basic pressure-bearing groove of the first multistage rectangular groove 408 to communicate the first multistage rectangular groove 408 with the first flow channel 404, and a second flow channel outlet 4052 is disposed at the bottom of the basic pressure-bearing groove of the second multistage rectangular groove 409 to communicate the second multistage rectangular groove 409 with the second flow channel 405.
As shown in fig. 20 to 21, the first and second multistage pressure receiving grooves are circular grooves, that is, the first multistage pressure receiving groove is a first multistage circular groove 410, the second multistage pressure receiving groove is a second multistage circular groove 411, the first and second multistage circular grooves 410 and 410 are respectively disposed at both parallel sides of the slipper 403, a first flow path outlet 4042 is disposed at the bottom of the basic pressure receiving groove of the first multistage circular groove 410 to communicate the first multistage circular groove 410 with the first flow path 404, and a second flow path outlet 4052 is disposed at the bottom of the basic pressure receiving groove of the second multistage circular groove 411 to communicate the second multistage circular groove 410 with the second flow path 405.
In order to simplify the processing technology, the first flow channel 404 and the second flow channel 405 can be formed by combining several straight channels when being processed, when the first flow channel 404 is processed, a hole is drilled downwards at a certain angle from the position of a first flow channel inlet 4041 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 to be communicated with the first flow channel inlet, then a first 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 to be communicated with the hole, and finally the hole opening of the lower end part of the sliding shoe 403 is blocked; the second fluid passage 405 is machined in the same way, and the second fluid passage inlet 4051 on the upper end face of the rotary disk 4 is drilled downwards at a certain angle, then the second fluid passage inlet is drilled upwards at a certain angle from the lower end of the sliding shoe 403 to be communicated with the sliding shoe 403, then the outlet hole 4052 of the second fluid passage is drilled and milled from the bottom of the fluid pressure bearing groove on the side face of the sliding shoe 403 to be communicated with the hole, and finally the opening of the lower end of the sliding shoe 403 is sealed.
Claims (5)
1. A static pressure support for a spherical pump rotor is characterized in that: the device comprises a first liquid flow channel (404) and a second liquid flow channel (405) which are arranged on a rotary disc (4) and liquid pressure bearing grooves which are arranged on two parallel side surfaces of a sliding shoe (403), wherein 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 the two parallel side surfaces of the sliding shoe (403); a sliding shoe lining plate (10) is arranged between two parallel side surfaces of the sliding shoe (403) and the side surface attached to the sliding groove (601); two parallel side surfaces of the sliding shoes (403) are attached to the sliding shoe lining plates (10) on the two sides and slide in the sliding grooves (601) in a reciprocating mode along the surfaces of the sliding shoe lining plates (10); the hydrostatic support is arranged between two parallel sides of the slipper (403) and the slipper liner plate (10).
2. A spherical pump rotor hydrostatic support as claimed in claim 1, wherein: the first liquid flow channel inlet (4041) is arranged on the upper end face of the rotary table (4) and communicated with one working chamber (1001), the first liquid flow channel outlet (4042) is arranged on one of two parallel side faces of the sliding shoe (403), and the first liquid flow channel inlet (4041) and the first liquid flow channel outlet (4042) are respectively positioned on two sides of a plane where the axis of the rotary table (4) is positioned and parallel to the two parallel side faces of the sliding shoe (403); the second liquid channel inlet (4051) is arranged on the upper end face of the rotary disc (4) and communicated with the other working chamber (1001), the second liquid 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 channel inlet (4051) and the second liquid channel outlet (4052) are respectively arranged on two sides of a plane where the axis of the rotary disc (4) is located and parallel to the two parallel side faces of the sliding shoe (403).
3. A spherical pump rotor hydrostatic support as claimed in claim 1, wherein: the fluid pressure-bearing grooves comprise a first fluid pressure-bearing groove (406) and a second fluid pressure-bearing groove (407) which are arranged on two parallel side surfaces of the sliding shoe (403), a first fluid flow channel outlet (4042) is communicated with the first fluid pressure-bearing groove (406), a second fluid flow channel outlet (4052) is communicated with the second fluid pressure-bearing groove (407), the cross-sectional size of the first fluid pressure-bearing groove (406) is larger than that of the first fluid flow channel outlet (4042), the cross-sectional size of the second fluid pressure-bearing groove (407) is larger than that 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 two sides of the sliding shoe.
4. A spherical pump rotor hydrostatic support as claimed in claim 1, wherein: the liquid bearing grooves comprise a first multi-stage bearing groove and a second multi-stage bearing groove which are arranged on two parallel side surfaces of the sliding shoe (403), a first liquid flow channel outlet (4042) is communicated with the first multi-stage bearing groove, a second liquid flow channel outlet (4052) is communicated with the second multi-stage bearing groove, the cross-sectional size of the first multi-stage bearing groove is larger than that of the first liquid flow channel outlet (4042), the cross-sectional size of the second multi-stage bearing groove is larger than that of the second liquid flow channel outlet (4052), and the surfaces of the first multi-stage bearing groove and the second multi-stage bearing groove are slightly lower than the planes on two sides of the sliding shoe (403); the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove respectively comprise a basic pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves, the basic pressure-bearing grooves are arranged in the centers of two parallel side surfaces of the sliding shoe (403), the bottom of the basic pressure-bearing groove is communicated with a first liquid flow channel outlet (4042) or a second liquid flow channel outlet (4052), 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 are sequentially wound around the periphery of the basic pressure-bearing groove.
5. A spherical pump rotor hydrostatic support as claimed in claim 1, wherein: the liquid pressure-bearing groove can be a circular groove or a rectangular groove, and the multistage liquid pressure-bearing groove can be a multistage circular groove or a multistage rectangular groove.
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 true CN110701040A (en) | 2020-01-17 |
| CN110701040B CN110701040B (en) | 2023-12-01 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2021083019A1 (en) * | 2019-11-01 | 2021-05-06 | 深圳市中安动力科技有限公司 | Spherical pump rotor static pressure support and spherical pump provided with static pressure support |
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