CN108691740B - Radial force balance double-sloping cam plate plunger type hydraulic motor pump - Google Patents
Radial force balance double-sloping cam plate plunger type hydraulic motor pump Download PDFInfo
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- CN108691740B CN108691740B CN201810643545.2A CN201810643545A CN108691740B CN 108691740 B CN108691740 B CN 108691740B CN 201810643545 A CN201810643545 A CN 201810643545A CN 108691740 B CN108691740 B CN 108691740B
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- plunger
- cylinder body
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- 238000005096 rolling process Methods 0.000 claims abstract description 31
- 230000009977 dual effect Effects 0.000 claims description 3
- 230000001360 synchronised effect Effects 0.000 claims description 3
- 238000005299 abrasion Methods 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 34
- 230000005540 biological transmission Effects 0.000 description 9
- 230000007246 mechanism Effects 0.000 description 7
- 238000001125 extrusion Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 239000013535 sea water Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 3
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 238000003825 pressing Methods 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
- 229910000897 Babbitt (metal) Inorganic materials 0.000 description 1
- 206010063385 Intellectualisation Diseases 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000013505 freshwater Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000006855 networking 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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2078—Swash plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention belongs to the field of plunger hydraulic pumps, and particularly discloses a radial force balance double-swash-plate plunger type hydraulic motor pump, which comprises a motor assembly and a hydraulic pump assembly, wherein the motor assembly comprises a motor shell, a left end cover and a right end cover which are arranged at two ends of the motor shell, and a motor stator and a motor rotor which are arranged in the motor shell; the hydraulic pump assembly comprises a cylinder body, a left swash plate and a right swash plate, the cylinder body is coaxially arranged with the motor shell, two ends of the cylinder body are in rotatable fit with the left end cover and the right end cover through rolling bearings, the cylinder body is connected with the motor rotor, the left swash plate and the right swash plate are respectively fixedly arranged on the left end cover and the right end cover, and the left swash plate and the right swash plate are respectively matched with plunger holes uniformly distributed on the left end surface and the right end surface inside the cylinder body through a left plunger reciprocating assembly and a right plunger reciprocating assembly; radial force balance pieces are arranged at the contact parts of the left swash plate and the right swash plate and the inner wall of the cylinder body. The invention can effectively balance the radial force born by the rolling bearing, reduce the abrasion of the bearing, prolong the service life, and has the advantages of high rotating speed, large flow and the like.
Description
Technical Field
The invention belongs to the field of plunger hydraulic pumps, and particularly relates to a radial force balance double-swash plate plunger type hydraulic motor pump.
Background
The hydraulic pump mainly has three forms, namely a gear pump, a vane pump and a plunger pump, wherein the plunger pump has the advantages of high-pressure transmission, abundant variable types, capacity of realizing the intellectualization and networking of variables, easiness in obtaining high flow rate and high rotating speed, convenience in arrangement, high total efficiency and the like, and can be structurally combined with any other form of pump.
Various structures of plunger pumps have been disclosed in the prior art, such as a double-swash-plate hydraulic motor plunger pump disclosed in patent CN102135082B, a double-swash-plate plunger type variable pump disclosed in CN104791210B, a plunger type motor pump disclosed in CN102619720B, etc., and the above-mentioned existing plunger pumps generally comprise a housing, a motor, an end cover, a plunger, a swash plate, a support bearing, etc., which are conventional mechanism components of the plunger pump. However, in order to realize high-pressure transmission, the support bearing of the rotating part of the plunger pump often bears large axial and radial loads during use, so that the bearing is severely worn, and finally the hydraulic pump cannot work. Meanwhile, with the development of mechanical equipment, the development of marine resources and the environmental protection, it is desired to directly use seawater as a hydraulic transmission medium to prevent pollution of hydraulic oil to the marine environment. However, the water hydraulic plunger pump currently faces the problems of large noise, low volumetric efficiency, short service life and the like, one of the key influencing factors is that the supporting bearing of the rotary part in the pump cannot form good lubrication due to low viscosity and strong corrosiveness of the seawater, the seawater can produce corrosion abrasion on the bearing metal materials, in addition, in the high-pressure transmission process, the supporting bearing bears high load, the service life of the bearing is greatly reduced, and finally the water hydraulic pump cannot work normally.
Therefore, how to reduce the axial force and the radial force born by the support bearing of the plunger pump rotary part in the high-pressure transmission process and improve the service life of the bearing is a problem to be solved in the field of plunger pumps.
Disclosure of Invention
Aiming at the defects or improvement demands of the prior art, the invention provides a radial force balance double-swash-plate plunger type hydraulic motor pump, which can effectively balance radial force born by rolling bearings at two ends of a cylinder body by arranging radial force balance pieces at the contact positions of two swash plates and the inner wall of the cylinder body, reduce bearing abrasion, prolong the service life of the bearings, have the advantages of high rotating speed, large flow, high power density and the like,
in order to achieve the above object, the present invention provides a radial force balance double swash plate plunger type hydraulic motor pump, which comprises a motor assembly and a hydraulic pump assembly, wherein:
the motor assembly comprises a motor shell, a left end cover and a right end cover which are arranged at two ends of the motor shell, and a motor stator and a motor rotor which are arranged inside the motor shell and are mutually matched;
the hydraulic pump assembly comprises a cylinder body, a left swash plate, a left plunger reciprocating assembly, a right swash plate and a right plunger reciprocating assembly, wherein the cylinder body is arranged in the motor shell and is coaxially arranged with the motor shell, two ends of the cylinder body are respectively in rotatable fit with the left end cover and the right end cover through rolling bearings, the cylinder body is connected with a motor rotor to realize synchronous rotation, the left swash plate and the right swash plate are respectively fixedly arranged on the left end cover and the right end cover, and are respectively matched with plunger holes uniformly distributed at the left end and the right end in the cylinder body through the corresponding left plunger reciprocating assembly and the right plunger reciprocating assembly, and the plunger holes at the left end and the right end are in one-to-one correspondence to form a plurality of plunger pairs;
the contact part of the left sloping cam plate and/or the right sloping cam plate and the inner wall of the cylinder body is provided with a radial force balancing piece for balancing the radial force born by the rolling bearing.
Further preferably, the radial force balance member is embedded at the thickest part of the left swash plate and/or the right swash plate, and the upper surface area of the radial force balance member is S 1 The lower surface is contacted with the inner wall surface of the cylinder body.
As a further preferable mode, the radial force balancing piece is internally provided with an oil guiding channel and an oil guiding hole communicated with the oil guiding channel, the upper surface of the radial force balancing piece is provided with an upper groove communicated with the oil guiding channel, the lower surface of the radial force balancing piece is provided with a lower groove communicated with the oil guiding channel, and a spring is arranged in the upper groove.
As a further preference, the bottom surface of the lower groove has an area S 2 The S is 2 Less than S 1 。
As a further preferable aspect, the inclination angles of the left and right swash plates are the same so that the axial forces of the two swash plates to the cylinder block cancel each other.
As a further preferable aspect, the rolling bearings at both ends of the cylinder are large-sized rolling bearings having an inner diameter of 170mm, an outer diameter of 260mm and a width of 42mm.
In general, compared with the prior art, the above technical solution conceived by the present invention mainly has the following technical advantages:
1. the radial force balance piece is arranged between the contact surfaces of the left swash plate, the right swash plate and the cylinder body, and can balance the radial force born by the rolling bearings supported on the two sides of most of the cylinder body, so that the abrasion of the bearings is reduced, and the service life of the bearings is prolonged.
2. The invention adopts a symmetrical structure with double swash plates, and the inclination angles of the left and right swash plates are the same, so that the axial load of the swash plates to the cylinder body can be well counteracted, the rolling bearing is free from the axial load, the abrasion of the bearing is further reduced, and the service life of the bearing is prolonged.
3. The two ends of the cylinder body of the invention use the large-size rolling bearing, the friction resistance is small, the starting performance and the bearing capacity are superior, the stable operation is ensured, the maintenance is convenient, and the working efficiency is improved.
4. The hydraulic pump part can be detached and refitted and then is independently connected with the common motor to be used as a common hydraulic pump.
5. The radial force balance double-swash-plate plunger type hydraulic motor pump designed by the invention has the advantages of high rotating speed, large flow, high power density and the like.
Drawings
FIG. 1 is a cross-sectional view of a radial force balanced dual swash plate plunger type hydraulic motor pump provided by an embodiment of the present invention;
FIG. 2 is a three-dimensional view of a radial force balance of the present invention;
FIG. 3 is a cross-sectional view of a radial force balance of the present invention;
FIG. 4 is a force analysis diagram of the left swash plate and radial force balance of the present invention;
FIG. 5 is a three-dimensional cross-sectional view of a radial force balanced dual swash plate plunger type hydraulic motor pump provided by an embodiment of the invention;
in the figure: the device comprises a left end cover 1, a motor housing 2, a rolling bearing 3, a radial force balancing piece 4, a cylinder 5, a motor stator 6, a motor rotor 7, a right end cover 8, a right swash plate 9, a right spherical hinge 10, a right plunger 11, an extrusion valve 12, a suction valve 13, a left plunger 14, a left spherical hinge 15 and a left swash plate 16.
Detailed Description
The present invention will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention. In addition, the technical features of the embodiments of the present invention described below may be combined with each other as long as they do not collide with each other.
As shown in fig. 1, the radial force balance double-swash-plate plunger type hydraulic motor pump provided by the embodiment of the invention comprises a motor assembly and a hydraulic pump assembly, wherein the motor assembly comprises a motor housing 2, a left end cover 1 and a right end cover 8 arranged at two ends of the motor housing 2, and a motor stator 6 and a motor rotor 7 which are arranged inside the motor housing 2 and are mutually matched.
As shown in fig. 1, the hydraulic pump assembly comprises a cylinder 5, a left swash plate 16, a left plunger reciprocating assembly 14, a right swash plate 9 and a right plunger reciprocating assembly 11, wherein the cylinder 5 is arranged inside the motor housing 2 and is positioned on the central axis of the motor housing 2, namely, the central axis of the cylinder 5 coincides with the central bearing of the motor housing 2, namely, the cylinder 5 and the motor housing are coaxially arranged, two ends of the cylinder 5 are supported by rolling bearings 3 so as to respectively realize rotatable matching with a left end cover 1 and a right end cover 8 through the rolling bearings, the cylinder 5 passes through a motor rotor 7 and is connected with the motor rotor 7 through keys so as to realize synchronous rotation, the left swash plate 16 and the right swash plate 9 are respectively fixedly arranged on the left end cover 1 and the right end cover 8, the outer wall surfaces of the left swash plate 16 and the right swash plate 9 are contacted with the inner wall surfaces of the cylinder 5, and the left swash plate 16 and the right swash plate 9 are respectively matched with plunger holes uniformly distributed on the left end surface and the right end surface inside the cylinder 5 through corresponding left plunger reciprocating assemblies and the right plunger reciprocating assemblies, and the plunger holes on the left end surface and the right end surface are in one-to-one correspondence to form a plurality of plunger pairs; the contact parts of the left swash plate 16 and the right swash plate 9 with the inner wall of the cylinder block 5 are provided with radial force balance pieces 4, and radial forces born by the rolling bearings 3 at the two ends of the cylinder block can be effectively balanced through the radial force balance pieces 4.
As shown in fig. 2 to 4, the radial force balance member 4 is fitted in a portion of the swash plate (the left swash plate 16 and the right swash plate 9) where the thickest portion contacts the cylinder block, and an upper surface 46 of the radial force balance member 4 faces the inner surface of the swash plate and serves as an upper support surface having an area S 1 The lower surface of the radial force balance 4 is in contact with the cylinder inner wall surface.
Specifically, as shown in fig. 2 and 3, the radial force balance member 4 is internally provided with an oil guiding channel 41 and an oil guiding hole 42 communicated with the oil guiding channel 41, external high pressure oil (high pressure liquid) can be guided into the oil guiding channel through the oil guiding hole 42, the upper surface of the radial force balance member 4 is provided with an upper groove 43, the lower surface is provided with a lower groove 44, both the upper groove 43 and the lower groove 44 are communicated with the oil guiding channel, wherein the upper groove faces a swash plate, a spring 45 is arranged in the upper groove and is in a compressed state and is used for providing pretightening force, the radial force balance member is propped against the inner wall of the cylinder body to prevent the radial force balance member from shaking, the lower groove faces the inner wall surface of the cylinder body, and the area of the bottom surface 47 of the lower groove is S 2 . Specifically, due to the pretightening force of the spring and the action of the rotating centrifugal force, the radial force balance piece is propped against the inner wall of the cylinder body, so that a certain gap exists on the upper surface of the radial force balance piece, high-pressure oil which is drained to the upper surface of the radial force balance piece by the oil drainage channel acts on the whole upper surface of the radial force balance piece, an oil film with a certain thickness is formed on the gap of the upper surface, and because the lower surface of the radial force balance piece is propped against the inner wall of the cylinder body, a gap is not formed between the lower surface of the radial force balance piece and the inner wall of the cylinder body, and the oil film is difficult to form, therefore, a lower groove is formed on the lower surface of the radial force balance piece, and the high-pressure oil forms the oil film on the lower groove. More specifically, make S 1 ＞S 2 Thereby, the acting force of the high-pressure oil on the upper surface of the radial force balance piece is larger than the acting force on the lower surface, and a resultant force F which is directed from the upper surface to the lower surface is generated, and the direction of the resultant force F is exactly equal to the radial force F exerted on the swash plate r In the opposite direction, thereby counteracting the radial force.
As shown in fig. 3, the radial force balance 4 has the following specific working principle: in the cylinder body rotating process, external high-pressure oil is fed into the oil guide channel through the oil guide hole, the high-pressure oil enters the upper groove and the lower groove of the radial force balancing piece through the oil guide channel, an upper high-pressure oil surface is formed between the upper supporting surface and the inner part of the sloping cam plate, a lower high-pressure oil surface is formed between the lower groove and the inner wall surface of the cylinder body, and the upper high-pressure oil surface has a downward acting area S facing the radial force balancing piece 1 The high pressure oil between the lower groove and the inner wall surface of the cylinder body has an upward acting area on the radial force balance memberS 2 Force due to S 1 ＞S 2 The combined acting force of the two is downward, so that a downward acting force F is generated on the cylinder body 5, the pressure of high-pressure oil can be adjusted according to the pressure of the transmission medium discharged by the motor pump, and then the radial acting force Fr of most swash plates 9 and 16 on the cylinder body 5 is balanced, and the radial force born by the rolling bearing 3 is reduced. When high-pressure oil is introduced into the radial force balance piece 4, the area of the upper surface of the radial force balance piece acting on the radial force balance piece is larger than the area of the lower groove acting, so that the radial force balance piece can be tightly pressed on the inner wall of the cylinder body to seal the liquid in the lower cavity, the radial force balance piece and the high-pressure oil in the lower groove can give a downward resultant force to the cylinder body, and the radial acting force generated by most of swash plates on the cylinder body is balanced, so that the radial force born by the rolling bearings supported at two ends of the cylinder body is reduced.
As shown in fig. 4, a is a swash plate fixed end, B is a plunger shoe assembly working surface, and a hydraulic supporting resultant force f=p of the radial force balance member (S 1 -S 2 ) -f, wherein: s is S 1 Is the area of the upper supporting surface S 2 The bottom area of the lower groove is p is high-pressure oil pressure, and f is the pre-compression force of the spring. Radial force F applied to the swash plate r ＝2tanβA 0 ∑p i Wherein: beta is the inclination angle of a sloping cam plate A 0 For a single plunger area, p i For the pressure in a single plunger cavity, i is the plunger cavity serial number of one end of the cylinder body, for example, 13 plunger cavities are arranged at the left end of the cylinder body, then the maximum value of i is 13, i=13 is the 13 th plunger cavity, and the hydraulic support combined force F and the radial force F applied by the swash plate r In opposite directions, the hydraulic supporting resultant force F balances the radial force F by introducing high-pressure oil r 。
Specifically, the left and right swash plates 16 and 9 are symmetrically arranged with the same inclination angle, so that the axial forces Fa of the left and right swash plates 16 and 9 to the cylinders 5 cancel each other out, thereby making the rolling bearings 3 supporting the cylinders 5 not receive the axial forces Fa.
Furthermore, the rolling bearings 3 at the two ends of the cylinder body 5 are large-size rolling bearings, the inner diameter of the rolling bearings is 170mm, the outer diameter of the rolling bearings is 260mm, the width of the rolling bearings is 42mm, the large-size rolling bearings 3 are used at the two ends of the cylinder body 5, compared with the existing common bearings, the large-size rolling bearings 3 can bear larger radial load, the friction resistance is small, the starting performance and the bearing capacity are superior, the running stability is guaranteed, and the maintenance is convenient.
More specifically, the left plunger reciprocating assembly comprises a left return mechanism and a plurality of left plungers 14 matched with a plurality of plunger holes uniformly distributed at the left end inside the cylinder body, the left return mechanism comprises a return disc and a left spherical hinge 15, the return disc is connected with the left swash plate and is in sliding fit with the plurality of left plungers 14, the left spherical hinge 15 is of a hollow structure, the head of the left spherical hinge is arc-shaped, the left spherical hinge is arranged at the left end of the cylinder body, the head of the left spherical hinge is hinged with the return disc, and each left plunger is assembled with each plunger hole. The right plunger reciprocating assembly structure is the same as the left plunger reciprocating assembly structure, the right plunger reciprocating assembly structure comprises a right return mechanism and a plurality of right plungers 11 matched with a plurality of plunger holes uniformly distributed at the right end inside the cylinder body, the right return mechanism comprises a return disc and a right spherical hinge 10, the return disc is connected with a right sloping cam plate and is in sliding fit with the plurality of right plungers 11, the right spherical hinge 10 is of a hollow structure, the head is arc-shaped, the right spherical hinge is arranged at the right end of the cylinder body, the head is hinged with the return disc, each right plunger is assembled with each plunger hole, the plungers at the left end and the right end of the cylinder body are coaxially corresponding to each other one by one to form a plurality of plunger pairs, and a suction valve 13 and an extrusion valve 12 which are communicated with the plunger holes are also arranged on the cylinder body corresponding to each pair of plungers for working medium to enter the cylinder body and discharge the cylinder body, wherein the suction valve is communicated with the plunger hole at the left end of the cylinder body, and the extrusion valve is communicated with the plunger hole at the right end of the cylinder body. When the motor is electrified and started, the motor rotor 7 drives the cylinder body 5 to synchronously rotate, and each plunger pair performs periodic reciprocating motion under the forced action of the two swash plates 9 and 16 and the return disc mechanisms 10 and 15, so that the volume of a plunger hole is periodically changed, corresponding suction valves and suction valves are alternately opened and closed, working medium on the left side of the cylinder body is sucked into a plunger cavity through the suction valves, and the working medium is pressed to the right side of the cylinder body from the plunger cavity through the pressing valves, so that the suction and pressing processes of the plunger pump are completed. The working principle of the above-described plunger pump is a conventional technology in the art, and thus the plunger reciprocating assembly is not limited to the above-defined structure, and any structure that can realize the above-described working process is applicable to the present invention.
The working process of the radial force balance double-swash-plate plunger type hydraulic motor pump is described below, referring to fig. 5, after the motor is powered on, the motor rotor 7 drives the cylinder body 5 to rotate clockwise through key connection, and under the combined action of the two swash plates 9 and 16 and the left and right return mechanisms 10 and 15, each plunger pair completes periodic reciprocating motion in the plunger holes, so that each plunger hole forms a pressure field with alternating height; with the rotation of the cylinder body 5, when the volume of the plunger cavity is continuously enlarged and the plunger cavity is in a low-pressure field, a valve core of a suction valve 13 of the flow distribution valve group is upwards opened, and a transmission medium flows into the corresponding plunger cavity from a suction inlet at the left end to finish the suction process of the plunger pump; with the continued rotation of the cylinder 5, when the volume of the plunger cavity with the suction action is continuously reduced and the plunger cavity is in a high-pressure field, the valve core of the suction valve 13 is closed downwards and pressed tightly, and the transmission medium is extruded from the plunger cavity through the extrusion valve 12 from the extrusion outlet, so that the extrusion action of the plunger pump is realized. During rotation, the radial force balance member 4 is fed with high-pressure oil (high-pressure liquid) to generate a downward acting force F on the cylinder 5, so as to balance the radial acting force Fr of most of swash plates 9 and 16 on the cylinder 5, and reduce the radial force applied by the rolling bearing 3.
The invention has compact structure, solves the problems of large radial load, serious bearing abrasion and the like of the traditional hydraulic pump by adopting the radial force balancing piece, can effectively reduce friction loss by adopting a rolling bearing mode, and can carry out forced convection cooling on the whole motor pump by adopting a working medium. The invention adopts the double-swash plate structure and the radial force balancing piece, can effectively improve the bearing force condition of the rolling bearing for supporting the cylinder body, and has the key part resistant to seawater corrosion. Therefore, the hydraulic pump of the invention can use hydraulic oil, or can use mediums such as fresh water or seawater as transmission mediums, and is suitable for marine underwater operation.
It will be readily appreciated by those skilled in the art that the foregoing description is merely a preferred embodiment of the invention and is not intended to limit the invention, but any modifications, equivalents, improvements or alternatives falling within the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (3)
1. The utility model provides a radial force balance double sloping cam plate plunger type hydraulic motor pump which characterized in that, includes motor assembly and hydraulic pump assembly, wherein:
the motor assembly comprises a motor shell (2), a left end cover (1) and a right end cover (8) which are arranged at two ends of the motor shell (2), and a motor stator (6) and a motor rotor (7) which are arranged inside the motor shell (2) and are mutually matched;
the hydraulic pump assembly comprises a cylinder body (5), a left swash plate (16), a left plunger reciprocating assembly, a right swash plate (9) and a right plunger reciprocating assembly, wherein the cylinder body (5) is arranged inside a motor shell (2) and is coaxially arranged with the motor shell (2), two ends of the cylinder body are respectively in rotatable fit with a left end cover (1) and a right end cover (8) through rolling bearings (3), the cylinder body (5) is connected with a motor rotor (7) to realize synchronous rotation, the left swash plate (16) and the right swash plate (9) are respectively fixedly arranged on the left end cover (1) and the right end cover (8), and the left swash plate (16) and the right swash plate (9) are respectively matched with plunger holes uniformly distributed at the left end and the right end inside the cylinder body (5) through corresponding left plunger reciprocating assembly (14) and right plunger reciprocating assembly (11), and each plunger hole at the left end and the right end corresponds to each plunger hole at each other to form a plurality of plunger pairs;
the contact part of the left swash plate (16) and/or the right swash plate (9) and the inner wall of the cylinder body (5) is provided with a radial force balancing piece (4) for balancing radial force born by the rolling bearing (3); the radial force balance piece (4) is embedded at the thickest part of the left swash plate (16) and/or the right swash plate (9), and the upper surface area of the radial force balance piece (4) is S 1 The lower surface is contacted with the inner wall surface of the cylinder body;
an oil guiding channel (41) and an oil guiding hole (42) communicated with the oil guiding channel (41) are formed in the radial force balancing piece (4), an upper groove (43) communicated with the oil guiding channel is formed in the upper surface of the radial force balancing piece (4), a lower groove (44) communicated with the oil guiding channel is formed in the lower surface of the radial force balancing piece, and a spring (45) is arranged in the upper groove;
the area of the bottom surface (47) of the lower groove is S 2 The S is 2 Less than S 1 。
2. A radial force balanced dual swash plate plunger type hydraulic motor pump according to claim 1, characterized in that the inclination angles of the left swash plate (16) and the right swash plate (9) are the same so that the axial forces of the two swash plates to the cylinder block (5) cancel each other.
3. Radial force balanced double swash plate plunger type hydraulic motor pump according to claim 1 or 2, characterized in that the rolling bearings (3) at both ends of the cylinder block (5) are large size rolling bearings with an inner diameter of 170mm, an outer diameter of 260mm and a width of 42mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810643545.2A CN108691740B (en) | 2018-06-21 | 2018-06-21 | Radial force balance double-sloping cam plate plunger type hydraulic motor pump |
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| CN201810643545.2A CN108691740B (en) | 2018-06-21 | 2018-06-21 | Radial force balance double-sloping cam plate plunger type hydraulic motor pump |
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| CN108691740B true CN108691740B (en) | 2024-03-26 |
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| CN109404242B (en) * | 2018-11-14 | 2024-02-06 | 华中科技大学 | Double-swash-plate three-oil-port shaft flow-distribution plunger type variable pump |
| CN109779869B (en) * | 2019-02-19 | 2024-02-02 | 华中科技大学 | High-power axial plunger type hydraulic pump similar to planetary gear train structure |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2103025U (en) * | 1991-09-29 | 1992-04-29 | 周其宁 | Two inclined plate large flow plunger-type fuel pump |
| CN1088662A (en) * | 1992-08-06 | 1994-06-29 | 大金工业株式会社 | Apparatus for producing of fluidic pressure |
| CN101328882A (en) * | 2008-07-02 | 2008-12-24 | 燕山大学 | Asynchronous sloping tray axial plunger piston hydraulic electric motor pump |
| CN106438259A (en) * | 2016-09-18 | 2017-02-22 | 华中科技大学 | Double-swash-plate plunger pump |
| CN208734500U (en) * | 2018-06-21 | 2019-04-12 | 华中科技大学 | A kind of balanced radial force two inclined plate plunger hydraulic electric-motor pump |
-
2018
- 2018-06-21 CN CN201810643545.2A patent/CN108691740B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2103025U (en) * | 1991-09-29 | 1992-04-29 | 周其宁 | Two inclined plate large flow plunger-type fuel pump |
| CN1088662A (en) * | 1992-08-06 | 1994-06-29 | 大金工业株式会社 | Apparatus for producing of fluidic pressure |
| CN101328882A (en) * | 2008-07-02 | 2008-12-24 | 燕山大学 | Asynchronous sloping tray axial plunger piston hydraulic electric motor pump |
| CN106438259A (en) * | 2016-09-18 | 2017-02-22 | 华中科技大学 | Double-swash-plate plunger pump |
| CN208734500U (en) * | 2018-06-21 | 2019-04-12 | 华中科技大学 | A kind of balanced radial force two inclined plate plunger hydraulic electric-motor pump |
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| CN108691740A (en) | 2018-10-23 |
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