CN111502951B - Roller type force balance unit pump - Google Patents
Roller type force balance unit pump Download PDFInfo
- Publication number
- CN111502951B CN111502951B CN201910099225.XA CN201910099225A CN111502951B CN 111502951 B CN111502951 B CN 111502951B CN 201910099225 A CN201910099225 A CN 201910099225A CN 111502951 B CN111502951 B CN 111502951B
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- Prior art keywords
- roller
- roller bracket
- bracket component
- piston
- cam
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- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims abstract description 22
- 230000005540 biological transmission Effects 0.000 claims abstract description 22
- 229910052802 copper Inorganic materials 0.000 claims abstract description 22
- 239000010949 copper Substances 0.000 claims abstract description 22
- 238000005096 rolling process Methods 0.000 claims abstract description 19
- 239000003921 oil Substances 0.000 claims description 98
- 230000033001 locomotion Effects 0.000 claims description 30
- 241000227287 Elliottia pyroliflora Species 0.000 claims description 24
- 230000001133 acceleration Effects 0.000 claims description 12
- 238000009434 installation Methods 0.000 claims description 7
- 238000007789 sealing Methods 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 5
- 230000008569 process Effects 0.000 claims description 5
- 239000010720 hydraulic oil Substances 0.000 claims description 2
- 238000005086 pumping Methods 0.000 claims description 2
- 230000000712 assembly Effects 0.000 claims 2
- 238000000429 assembly Methods 0.000 claims 2
- 230000008878 coupling Effects 0.000 description 13
- 238000010168 coupling process Methods 0.000 description 13
- 238000005859 coupling reaction Methods 0.000 description 13
- 230000008859 change Effects 0.000 description 4
- 238000004891 communication Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
Classifications
-
- 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
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/20—Other positive-displacement pumps
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The roller type force balance unit pump is provided with a rolling bearing between the right coupler and the right roller component; the left cam and the right cam are symmetrically distributed on two sides of the pump core assembly, and the phase difference is 90 degrees; the roller assembly rolls on the cam surface, four cone rollers are distributed on one side, two groups of copper sleeves of the pump core assembly are fixed on the C-shaped roller support through pin shafts, two pairs of rectangular high-low pressure oil holes are circumferentially and uniformly distributed on the copper sleeves and the cylinder body, and the copper sleeves are respectively contacted with a first distribution groove and a second distribution groove on the piston to absorb and discharge oil; an annular oil groove communicated with the high-pressure oil holes is formed in the cylinder body, and oil flowing out of the two high-pressure oil holes is converged; the rotor mass formed by the first roller bracket component, the third roller bracket component, the transmission shaft and the left and right concentric rings is equal to the sum of the rotor mass formed by the second roller group, the fourth roller bracket component and the piston; the first high-low pressure cavity in the pump core is communicated with the first distributing groove of the piston all the time, and the second high-low pressure cavity is communicated with the second distributing groove of the piston all the time.
Description
Technical Field
The invention relates to a hydraulic plunger pump, which belongs to a hydraulic pump and a hydraulic motor in the field of fluid transmission and control.
Background
The hydraulic pump is used as a power element of a hydraulic system, can transmit mechanical energy of a prime motor or other external energy to liquid, increases the energy of the liquid, and is widely applied to engineering machinery and aerospace. The traditional plunger pump has the problems of low efficiency, large vibration, high noise, low service life and the like due to the limitations of friction pairs, size and the like, and the aims of high speed and high pressure are difficult to realize.
The traditional common axial plunger pump has more parts which move relatively in the axial plunger pump, has high requirements on material quality and processing precision, is sensitive to oil pollution, has higher requirements and cost for processing, using and maintaining, and has high price; the cylinder body rotates along with the transmission shaft, and the moment of inertia is large, so that the response speed of starting, stopping and speed regulation is slow, and the output flow of the pump is not controlled by speed regulation; the friction pairs in the cylinder body are more, the temperature rise of the cylinder body is quicker under high-speed rotation, and the abrasion of parts such as a valve plate, a plunger and the like directly affects the service life and the durability of the pump. Besides, due to the limitation of the working principle of the plunger pump, the transmission shaft rotates for one circle, each plunger can only realize one oil suction and one oil discharge, and the displacement of the plunger pump is limited.
Because of various drawbacks of the conventional plunger pump, patent document CN205895515U proposes a hydraulic pump of a novel structure, which can realize the oil sucking and discharging function by axially moving while rotating by using the motion principle of two degrees of freedom of the piston, and is named as a two-dimensional 2D piston pump because of the motion in two dimensions during operation. The double-freedom-degree motion principle is applied to the design of a piston of a pump, and a novel flow distribution mode is formed.
Disclosure of Invention
In order to overcome the defects of the conventional two-dimensional 2D piston pump, the invention provides the roller type force balance unit pump which can axially move to realize a continuous oil sucking and discharging function while the plunger rotates by utilizing the double degrees of freedom of the piston.
The technical implementation scheme of the invention is as follows:
The roller type force balance unit pump sequentially distributes a right end cover, a right coupler assembly, a right roller assembly, a right cam and a pump shell along the axial direction, and comprises a pump core assembly, a left cam, a left roller assembly, a left coupler assembly and a left end cover. The left end cover and the right end cover are coaxially distributed with the left coupler and the right coupler and are isolated by adopting rolling bearing movement. A rolling bearing is arranged between the right coupler and the right roller assembly to prevent direct contact with the right roller assembly. The left cam and the right cam are symmetrically distributed on two sides of the pump core assembly, and the phase difference is 90 degrees. The roller assembly rolls on the cam surface, four cone rollers are distributed on one side, two groups of pin shafts are utilized to be fixed on the C-shaped roller support, a group of rollers which are in contact with the right cam and have C-shaped openings towards the cam surface are the first roller support assembly, the first roller support assembly comprises a pair of cone rollers, a C-shaped roller support, rolling bearings and fixed pin shafts which are symmetrically distributed along the axis of the pump mandrel, a group of rollers which are in contact with the right cam and have C-shaped openings opposite to the cam surface are the second roller support assembly, and the second roller support assembly comprises a pair of cone rollers, roller supports, rolling bearings and fixed pin shafts which are symmetrically distributed along the axis of the pump mandrel. The two groups of roller bracket components are fixed in the circumferential direction and move axially relative to each other. The idler wheel is fixed on the idler wheel frame by adopting a pin shaft mode. The group of rollers which are contacted with the left cam and the C-shaped opening faces the cam surface is a third roller bracket component, and the group of rollers which are contacted with the left cam and the C-shaped opening faces away from the cam surface is a fourth roller bracket component. The second roller bracket component and the fourth roller bracket component are fixed on the piston in a spline mode, and the first roller bracket component and the third roller bracket component are fixed on the transmission shaft in a spline mode. The third roller bracket component is consistent with the first roller bracket component in installation mode and movement mode, and the fourth roller component is consistent with the second roller component. The installation phase angles of the first roller bracket component and the second roller bracket component differ by 90 degrees, the phase positions of the first roller bracket component and the third roller bracket component are the same, and the phase positions of the second roller bracket component and the fourth roller bracket component are the same.
The pump core assembly comprises a cylinder body, a piston, a copper sleeve, a transmission shaft, a left concentric ring and a right concentric ring. And spline shafts are formed at two ends of the piston, and the second roller bracket assembly and the fourth roller bracket assembly are fixed. The wall surface of the piston is provided with a pair of first distributing grooves and a pair of second distributing grooves, the first distributing grooves and the second distributing grooves are alternately and uniformly distributed, the first distributing grooves and the second distributing grooves are U-shaped distributing grooves with opposite axial openings, and the width of the U-shaped distributing grooves is consistent with the width of the rectangular holes on the copper sleeve. The left concentric ring and the right concentric ring are respectively sleeved on steps at two sides of the piston, the installation directions are axially opposite, and the left concentric ring and the right concentric ring are fixed on the first roller bracket component and the third roller bracket component by using fixed pin shafts. The outer circle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston axially move relatively. Spline shafts are formed at two ends of the transmission shaft, and the first roller bracket component and the third roller bracket component are fixed. Two pairs of rectangular high-low pressure oil holes uniformly distributed in the circumferential direction are formed in the copper sleeve and the cylinder body and are respectively contacted with a first distributing groove and a second distributing groove on the piston to suck and discharge oil. The cylinder body is provided with an annular oil groove communicated with the high-pressure oil holes, and oil flowing out of the two high-pressure oil holes is converged.
The rotor mass formed by the first roller bracket component, the third roller bracket component, the transmission shaft and the left concentric ring and the right concentric ring is equal to the sum of the rotor mass formed by the second roller group, the fourth roller bracket component and the piston, and the inertial force generated by acceleration is balanced on the cam.
The left side surface of the right concentric ring, the outer surface of the piston and the inner side surface of the copper bush in the pump core form a first high-low pressure cavity, the right side surface of the left concentric ring, the outer surface of the piston and the inner side surface of the copper bush form a second high-low pressure cavity, the inner circles of the left concentric ring and the right concentric ring are in clearance fit with the piston, and the outer circle is in clearance fit with the inner side surface of the copper bush to form clearance seal. The first high-low pressure cavity is communicated with the first distributing groove of the piston all the time, and the second high-low pressure cavity is communicated with the second distributing groove of the piston all the time.
In the process of moving the first roller bracket component from the lowest point to the highest point of the right cam, the concentric rings are driven to rotate in the same direction and move rightwards, the second roller bracket component moves from the highest point to the lowest point of the right cam, the piston is driven to move leftwards, and the first distributing groove on the piston is communicated with the copper sleeve and the oil suction hole on the cylinder body to suck oil into the first high-low pressure cavity. The first roller support assembly rotates and drives the transmission shaft to synchronously rotate and move rightwards through the spline, the movement is transmitted to the third roller support assembly, and the third roller support assembly moves from the highest point of the left cam to the lowest point to drive the left concentric ring to move rightwards. The second roller bracket component transmits the motion to the fourth roller bracket component through a spline on the piston to drive the piston to move leftwards, the volume in the second high-low pressure cavity is reduced, and oil is discharged from the oil outlet through a second distributing groove on the piston. Along with the rotary motion of the roller assembly, the first distributing groove and the second distributing groove are periodically changed with the oil suction holes and the oil discharge holes on the concentric rings, so that the pumping oil discharge of the roller type inertial force balancing unit is realized.
Further, the left end cover is fixed on the left side face of the pump shell through bolts, and the right end cover is fixedly connected on the right end face of the pump shell through bolts. The left end cover, the right end cover and the pump shell are sealed by sealing rings. The cylinder body is fixedly connected to the right end face of the pump shell through bolts, and the cylinder body is sealed with the pump shell through a sealing ring.
Further, the positions of the oil suction and discharge holes on the copper bush and the positions of the oil suction and discharge holes on the cylinder body are completely consistent, and the outer circle of the copper bush and the inner circle of the cylinder body are fixed in an interference fit mode.
The beneficial effects of the invention are mainly shown in the following steps:
1. the volume change is completed by the cooperation of the piston and the concentric rings, and compared with the volume change of a single piston, the volume change is doubled, and the space is saved. When the stroke and the displacement are unchanged, the cross section area is reduced, so that the stress of the guide rail and the conical roller is reduced, and high load is easy to realize.
2. The roller wheel rotating mode is adopted, and compared with a cam rotating type force balance unit pump, the structure is simple, and the movement reliability is greatly enhanced.
3. By utilizing the inertial force of different roller groups in opposite directions and balancing the mass of different rotors, the inertial force received on the cylinder body can be balanced, the mechanical vibration during operation is reduced, the output rotating speed of the motor is more stable, and the flow pulsation is reduced. Meanwhile, the output torque of the motor can be reduced, and the energy is saved.
4. Through special shaft coupling structure, wrap up rotor part in airtight intracavity, greatly reduced the stirring oil loss that produces when the rotor rotates, improve the mechanical efficiency of pump.
Drawings
Fig. 1 is a schematic diagram of the roller type force balance unit pump assembly of the present invention.
Fig. 2 is a schematic view of the internal assembly of the present invention.
Fig. 3a to 3b are schematic views of the right coupling assembly of the present invention, wherein fig. 3a is an inner side view of the right coupling assembly, and fig. 3b is an outer side view of the right coupling assembly.
Fig. 4a to 4b are schematic views of the left coupling assembly of the present invention, wherein fig. 4a is an inner side view of the left coupling assembly, and fig. 4b is an outer side view of the left coupling assembly.
Fig. 5a to 5b are schematic views of the structure of the left end cap of the present invention, wherein fig. 5a is an outer side view of the left end cap, and fig. 5b is an inner side view of the left end cap.
Fig. 6 is a schematic view of the right end cap structure of the present invention.
Fig. 7a to 7d are schematic views of a roller assembly according to the present invention, wherein fig. 7a is a schematic view of the roller assembly, fig. 7B is an end view of the roller assembly, fig. 7C is a C-C sectional view of fig. 7B, and fig. 7d is a B-B sectional view of fig. 7B.
FIG. 8 is a schematic illustration of concentric ring structures of the present invention.
Fig. 9 is a schematic view of the piston structure of the present invention.
Fig. 10 is a schematic view of the structure of the propeller shaft of the present invention.
Fig. 11 is a schematic diagram of the roller assembly coupling arrangement of the present invention.
Fig. 12 is a schematic view of a pump core assembly of the present invention.
Fig. 13a to 13c are schematic structural views of a cylinder copper sheathing assembly according to the present invention, fig. 13a is an end view of the cylinder copper sheathing assembly, fig. 13b is a side view of the cylinder copper sheathing assembly, and fig. 13c is a sectional view of fig. 13b from A-A.
Fig. 14a to 14c are schematic views of the cam structure of the present invention, fig. 14a is a front view of the cam, fig. 14b is a side view of the cam, and fig. 14c is a rear view of the cam.
Fig. 15a to 15b are schematic diagrams of the pump casing structure of the present invention, fig. 15a is a front view of the pump casing structure, and fig. 15b is a sectional view taken from A-A of fig. 15 a.
Fig. 16a to 16e are different angle flow channel sectional views of the present invention, in which fig. 16a is a flow channel sectional view when the rotation angle is 0 °, fig. 16b is a flow channel sectional view when the rotation angle is 45 °, fig. 16c is a flow channel sectional view when the rotation angle is 90 °, fig. 16d is a flow channel sectional view when the rotation angle is 135 °, and fig. 16e is a flow channel sectional view when the rotation angle is 180 °.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
The roller type force balance unit pump of the present invention includes: right coupler assembly 1R, right end cap 3, left roller assembly 4L and right roller assembly 4R, pump core assembly 5, pump housing 6, left end cap 8, left coupler 1L. The right end cover 3 is connected with the right end face of the pump shell 6 through bolts, and the left end cover 8 is fastened on the left end face of the pump shell 6 through bolts. The sealing between the right end cover 3 and the pump housing 6 and between the left end cover 8 and the pump housing 6 is mainly by the sealing ring 7. The right coupler 1R and the right end cover 3 are ensured to be axially positioned through the rolling ball bearing 10, the motion isolation of the right coupler 1R and the right end cover 3 is realized through the rolling ball bearing 10, and the right coupler 1R can complete the rotation motion. The right coupling 1R and the right end cover 3 are sealed mainly by gaps, and the trapezoid groove 2 on the right end cover 3 is used for preventing volatile harmful gases in oil from escaping. Four rolling bearings 12 are uniformly distributed on the inner wall surface of the right coupling component 1R and are fixed on the coupling 11 through pin shafts 13, and the right coupling component 1R is contacted with the right roller component 4R through the rolling bearings 12, so that no relative sliding exists when the right roller component 4R and the right coupling component 1R do relative axial movement. Four rolling bearings 12 are interposed between the first roller bracket assembly 14 and the second roller bracket assembly 15.
The right roller assembly 4R includes a first roller bracket assembly 14, a second roller bracket assembly 15, and a right concentric ring 172. The first roller bracket assembly 14 includes a roller 144, a rolling bearing 1414, a first roller bracket 142, and a fixed pin 143. The roller 144 and the rolling bearing 141 are fixed to the first roller bracket 142 through a fixed pin 143. The first roller support assembly 14 is fixed on the transmission shaft 16 through a spline 16a, the right concentric ring 172 is fixed on the first roller support 141 through a pin hole 172a and a fixed pin shaft 143, and the transmission shaft 16, the right concentric ring 172 and the first roller support assembly 14 are fixedly connected and do synchronous motion. The second roller bracket assembly 15 includes a rolling bearing 151, a second roller bracket 152, a fixed pin 153, and a roller 154. The rolling bearing 151 and the roller 154 are fixed on the second roller bracket 152 through a fixed pin. The second roller assembly 15 and the piston 18 are fixedly connected through a spline 18a and synchronously move. The first roller bracket assembly 14 and the second roller bracket assembly 15 are synchronously rotated by the circumferential constraint of the rolling bearing 12, but there is no axial constraint, i.e., the first roller bracket assembly 14 and the second roller bracket assembly 15 allow for axial relative movement. The right roller assembly 4R and the left roller assembly 4L are consistent in installation, positioning and movement relationship, and two pairs of rollers in the same direction are regarded as the same assembly.
The pump core assembly 5 comprises a transmission shaft 16, a piston 18, a right concentric ring 172, a left concentric ring 171, a right cam 19R, a left cam 19L, a filter screen 20, a cylinder 21, and a copper sleeve 22. The cylinder 21 is fixed by bolts through the through holes 21a and the threaded holes 6a on the pump shell 6, so as to realize the positioning of the pump core assembly. The right cam 19R has a registration pin hole 19Ra and is fixed to a registration pin hole 21e in the cylinder 21 using a registration pin shaft. The cam travel can be divided into two parts according to the shape of the cam surface of the right cam 19R, with the lift being from the lowest point to the highest point, the return being from the highest point to the lowest point, the highest point being the peak point, the lowest point being the valley point, each cam having two peak points, two valley points, that is, each cam having two lift steps, two return steps, each step being 90 °. The copper bush 22 is fixed in the inner ring of the cylinder body 21 in an interference fit manner, and a high-pressure oil hole 22a and a low-pressure oil hole 22b in the copper bush 22 are respectively communicated with a high-pressure oil hole 21b and a low-pressure oil hole 21c in the cylinder body 21. The annular groove 21d in the cylinder 21 is communicated with the oil drain port 6b on the pump shell, and oil can flow out from the two high-pressure oil holes 22a of the cylinder 21, and flow out from the oil drain port 6b on the pump shell after converging together through the annular groove 21 d.
The roller type force balance unit pump left cam 19L and right cam 19R are installed with a phase difference of 90 °, i.e. the peak point of the left cam 19L is opposite to the valley point of the right cam 19R, the lift of the left cam 19L is opposite to the return stroke of the right cam 19R, the first roller bracket assembly 14 and the second roller bracket assembly 15 are installed with a phase difference of 90 °, when the first roller assembly 14 moves from the valley point to the peak point along the right cam 19R while moving from the peak point to the valley point along the left cam 19L, and the second roller assembly 15 moves from the peak point to the valley point along the left cam 19L while moving from the valley point to the peak point along the right cam 19R. The left cam 19L and the right cam 19R are a pair of identical cams, the installation phase angles of which differ by 90 °, and the change rules of the cam curved surfaces are also identical. The cam curved surface adopts equal acceleration and other speed reduction motion rules, the first roller component 14 performs uniform rotation motion in the circumferential direction, in the process of moving from a valley point to a peak point along the right cam curved surface, the axial direction performs uniform acceleration motion with fixed acceleration, the speed direction is rightward, the acceleration path is 45 degrees of rotation angle, then the uniform speed reduction motion is started, the speed direction is unchanged, the acceleration direction is leftward, the speed reduction path is 45 degrees of rotation angle, and the speed is just 0 with the valley point when the first roller bracket component 14 reaches the peak point of the right cam 19R. The second roller support assembly 15 and the first roller support assembly 14 rotate synchronously, in the process of moving from the valley point to the peak point along the curved surface of the left cam, uniform acceleration movement is carried out by axial direction with fixed acceleration, the speed direction is leftwards, the acceleration path is 45 degrees, then uniform deceleration movement is carried out, the speed direction is unchanged, the acceleration direction is rightwards, the deceleration path is 45 degrees, and the speed is just 0 as the valley point until the second roller support assembly 15 reaches the peak point of the left cam 19L. The acceleration applied to the first roller bracket assembly 14 and the second roller bracket assembly 15 during the movement process is the same and opposite. When the sum of the masses of the first roller bracket assembly 14, the transmission shaft 16, the left concentric ring 171 and the right concentric ring 172 is equal to the sum of the masses of the second roller bracket assembly 15 and the piston 18, the inertial force of the first roller bracket assembly 14 acting on the cam is opposite to the inertial force of the second roller bracket assembly acting on the cam in the same direction, and the inertial force indirectly acting on the cylinder body and the pump shell is offset, so that the balance of the inertial force is realized.
The roller type force balance unit pump left end cover 8 is connected with an external oil way, hydraulic oil enters the pump shell through four waist-shaped holes 8a on the left end cover 8 and fills a left cavity in the left end cover 8, oil enters a right cavity in the right end cover 3 on one hand through a connecting hole 21f on the cylinder body 21, and oil in the two cavities can play a role in lubricating friction pairs. On the other hand, the oil enters the first high-low pressure cavity B or the second high-low pressure cavity A through the connecting hole 21f, the low-pressure oil hole 21c of the cylinder body and the low-pressure oil hole 22B on the copper bush and the first distributing groove 18c or the second distributing groove 18B on the piston 18 connected with the low-pressure oil hole 22B on the copper bush. The high-pressure oil enters the annular groove 21d of the cylinder body 21 from the second high-low pressure cavity A or the first high-low pressure cavity B through the second distributing groove 18B or the first distributing groove 18c on the piston 18 and the high-pressure oil hole 22a and the high-pressure oil hole 21B connected with the second distributing groove 18B or the first distributing groove, and is discharged out of the unit pump through the oil discharge port 6B on the pump shell 6. The second high-low pressure cavity A is a closed cavity formed by enclosing the inner circular surface of the copper sleeve 22, the right side end surface of the left concentric ring 161 and the piston 18, and the first high-low pressure cavity B is a closed cavity formed by enclosing the inner circular surface of the copper sleeve 22, the left side end surface of the right concentric ring 172 and the piston 18.
Principle of operation
The roller type force balance unit pump drives the right coupler assembly 1R in the right end cover 3 to rotate through an external motor, and then drives the first roller bracket assembly 14 and the second roller bracket assembly 15 to do synchronous rotary motion, the first roller bracket assembly 14 moves rightwards under the constraint of the right cam 19R, the right concentric ring 172 is driven to move rightwards through the fixed constraint pin shaft 143, meanwhile, the second roller bracket assembly 15 moves leftwards under the constraint of the left cam 19L, and the piston 18 is driven to move leftwards through the fixed connection 18a, so that the volume of the first high-low pressure cavity B is increased, and the volume of the second high-low pressure cavity A is reduced. The oil outside oil duct enters the left end cover 8, enters the inside of the left end cover through the waist-shaped hole 8a on the left end cover 8, enters the low-pressure oil hole 22B on the copper bush 22 through the connecting holes 21f and 21c on the cylinder body 21, and at the moment, the first distributing groove 18c on the piston is connected with the low-pressure oil hole 22B on the copper bush, and the oil is sucked into the first high-low pressure cavity B through the first distributing groove 18 c. The volume of the second high-low pressure cavity A is reduced, so that the oil pressure in the second high-low pressure cavity A is increased, and the oil is pressed into the annular groove 22d through the second distributing groove 18b on the piston, the high-pressure oil hole 22a on the copper sleeve 22 and the high-pressure oil hole 21b on the cylinder body, and is discharged through the oil discharge port on the pump shell 6.
When the first roller bracket assembly 14 rotates by 45 degrees, the first roller bracket assembly 14 moves to the limit position under the constraint of the right cam 19R, namely, the right end of the row Cheng Zui, the second roller bracket assembly 15 moves to the leftmost end of the stroke under the constraint of the left cam 19L, at this time, the first high-low pressure cavity B is in the maximum volume state, the second high-low pressure cavity A is in the minimum volume state, the communication area between the second distributing groove 18B and the high-pressure oil hole 22a and the low-pressure oil hole 22B on the copper bush, and the communication area between the first distributing groove 18c and the high-pressure oil hole 22a and the low-pressure oil hole 22B on the copper bush are zero. Then, the first roller bracket assembly 14 moves leftwards under the constraint of the left cam 19L, and the second roller bracket assembly 15 moves leftwards under the constraint of the right cam 19R, so that the volume of the second high-low pressure chamber a increases, and the volume of the first high-low pressure chamber B decreases. The oil outside oil duct enters the left end cover 8, enters the inside of the left end cover through the waist-shaped hole 8a on the left end cover 8, enters the low-pressure oil hole 22b on the copper sleeve 22 through the connecting holes 21f and 21c on the cylinder body 21, and at the moment, the second distributing groove 18b on the piston is connected with the low-pressure oil hole 22b on the copper sleeve, and sucks the oil into the second high-low pressure cavity A through the second distributing groove 18 b. The volume of the first high-low pressure cavity B is reduced, so that the oil pressure in the first high-low pressure cavity B is increased, and the oil is pressed into the annular groove 22d through the first distributing groove 18c on the piston, the high-pressure oil hole 22a on the copper sleeve 22 and the high-pressure oil hole 21B on the cylinder body, and is discharged through the oil discharge port on the pump shell 6.
When the first roller bracket assembly 14 and the second roller bracket assembly 15 are simultaneously in the middle position when rotated by 90 degrees, at this time, the second distributing groove 18b on the piston and the high-pressure oil hole 22a on the copper bush, and the first distributing groove 18c and the low-pressure oil hole 22b on the copper bush are in the maximum contact state. The first roller bracket assembly 14 still moves leftwards under the constraint of the left cam 19L, and the second roller bracket assembly 15 still moves leftwards under the constraint of the right cam 19R, so that the volume of the second high-low pressure cavity a continues to be increased, and the volume of the first high-low pressure cavity B continues to be reduced.
When the first roller bracket assembly 14 rotates by 135 degrees, the first roller bracket assembly 14 moves to the leftmost end of the stroke under the constraint of the left cam 19L, the second roller bracket assembly 15 moves to the rightmost end of the stroke under the constraint of the right cam 19R, the second high-low pressure cavity A is in the maximum volume state, the first high-low pressure cavity B is in the minimum volume state, at this time, the communication area between the second distributing groove 18B and the high-pressure oil hole 22a and the low-pressure oil hole 22B on the copper bush and the communication area between the first distributing groove 18c and the high-pressure oil hole 22a and the low-pressure oil hole 22B on the copper bush are zero. The first roller bracket assembly 14 moves rightward under the constraint of the right cam 19R, and the second roller bracket assembly 15 moves leftward under the constraint of the left cam 19L, so that the volume of the first high-low pressure chamber B increases, and the volume of the second high-low pressure chamber a decreases. The oil outside oil duct enters the left end cover 8, enters the inside of the left end cover through the waist-shaped hole 8a on the left end cover 8, enters the low-pressure oil hole 22B on the copper bush 22 through the connecting holes 21f and 21c on the cylinder body 21, and at the moment, the first distributing groove 18c on the piston is connected with the low-pressure oil hole 22B on the copper bush, and the oil is sucked into the first high-low pressure cavity B through the first distributing groove 18 c. The volume of the second high-low pressure cavity A is reduced, so that the oil pressure in the second high-low pressure cavity A is increased, and the oil is pressed into the annular groove 22d through the second distributing groove 18b on the piston, the high-pressure oil hole 22a on the copper sleeve 22 and the high-pressure oil hole 21b on the cylinder body, and is discharged through the oil discharge port on the pump shell 6.
And then the roller type force balance unit pump is driven by the motor to circularly perform the periodic motion, and the roller component of the roller type force balance unit pump completes axial reciprocating motion completed twice when the motor rotates for one period, namely 360 degrees, and the first high-low pressure cavity A and the second high-low pressure cavity B complete oil suction and discharge twice respectively.
The embodiments described in the present specification are merely examples of implementation forms of the inventive concept, and the scope of protection of the present invention should not be construed as being limited to the specific forms set forth in the embodiments, and the scope of protection of the present invention and equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.
Claims (2)
1. Roller formula force balance unit pump, its characterized in that: a right end cover, a right coupler assembly, a right roller assembly, a right cam, a pump shell, a pump core assembly, a left cam, a left roller assembly, a left coupler assembly and a left end cover are sequentially distributed along the axial direction; the left end cover and the right end cover are coaxially distributed with the left coupler assembly and the right coupler assembly, and are isolated by adopting rolling bearing movement; a rolling bearing is arranged between the right coupler component and the right roller component; the left cam and the right cam are symmetrically distributed on two sides of the pump core assembly, and the phase difference is 90 degrees; the roller assembly rolls on the cam surface, four cone rollers are distributed on one side, two groups of the cone rollers are fixed on a C-shaped roller support through pin shafts, one group of rollers which are contacted with the right cam and have C-shaped openings towards the cam surface are first roller support assemblies, each first roller support assembly comprises a pair of cone rollers, a C-shaped roller support, a rolling bearing and a fixed pin shaft which are symmetrically distributed along the axis of the pump mandrel, one group of rollers which are contacted with the right cam and have C-shaped openings opposite to the cam surface are second roller support assemblies, and each second roller support assembly comprises a pair of cone rollers, roller supports, rolling bearings and fixed pin shafts which are symmetrically distributed along the axis of the pump mandrel; the two groups of roller bracket components are fixed in the circumferential direction and move axially relatively; the idler wheel is fixed on the idler wheel frame in a pin shaft mode; the group of rollers which are contacted with the left cam and the C-shaped opening faces the cam surface is a third roller bracket component, and the group of rollers which are contacted with the left cam and the C-shaped opening faces away from the cam surface is a fourth roller bracket component; the second roller bracket component and the fourth roller bracket component are fixed on the piston in a spline mode, and the first roller bracket component and the third roller bracket component are fixed on the transmission shaft in a spline mode; the mounting mode and the movement mode of the third roller bracket component are consistent with those of the first roller bracket component, and the fourth roller bracket component is consistent with that of the second roller bracket component; the installation phase angles of the first roller bracket component and the second roller bracket component differ by 90 degrees, the phase positions of the first roller bracket component and the third roller bracket component are the same, and the phase positions of the second roller bracket component and the fourth roller bracket component are the same;
The pump core assembly comprises a cylinder body, a piston, a copper sleeve, a transmission shaft, a left concentric ring and a right concentric ring; the two ends of the piston are made into spline shafts, and the second roller bracket component and the fourth roller bracket component are fixed; the wall surface of the piston is provided with a pair of first distributing grooves and a pair of second distributing grooves, the first distributing grooves and the second distributing grooves are alternately and uniformly distributed, the first distributing grooves and the second distributing grooves are U-shaped distributing grooves with opposite axial openings, and the width of the U-shaped distributing grooves is consistent with the width of the rectangular holes on the copper sleeve; the left concentric ring and the right concentric ring are respectively sleeved on steps at two sides of the piston, the installation directions are axially opposite, and the left concentric ring and the right concentric ring are fixed on the first roller bracket component and the third roller bracket component by using fixed pin shafts; the outer circle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston axially move relatively; two ends of the transmission shaft are made into spline shafts, and the first roller bracket component and the third roller bracket component are fixed; two pairs of rectangular high-low pressure oil holes uniformly distributed in the circumferential direction are formed in the copper sleeve and the cylinder body and respectively contact with the first and second distributing grooves on the piston to suck and discharge oil; an annular oil groove communicated with the high-pressure oil holes is formed in the cylinder body, and oil flowing out of the two high-pressure oil holes is converged;
The mass of the rotor formed by the first roller bracket component, the third roller bracket component, the transmission shaft and the left and right concentric rings is equal to the sum of the mass of the rotor formed by the second roller bracket component, the fourth roller bracket component and the piston, and the inertial force generated by acceleration is balanced on the cam;
the left side surface of the right concentric ring, the outer surface of the piston and the inner side surface of the copper bush in the pump core form a first high-low pressure cavity, the right side surface of the left concentric ring, the outer surface of the piston and the inner side surface of the copper bush form a second high-low pressure cavity, the inner circles of the left concentric ring and the right concentric ring are in clearance fit with the piston, and the outer circles of the left concentric ring and the right concentric ring are in clearance fit with the inner side surface of the copper bush to form clearance seal; the first high-low pressure cavity is communicated with the first distributing groove of the piston all the time, and the second high-low pressure cavity is communicated with the second distributing groove of the piston all the time;
in the process that the first roller bracket component moves from the lowest point to the highest point of the right cam, the concentric rings are driven to rotate in the same direction and move rightwards, the second roller bracket component moves from the highest point to the lowest point of the right cam, the piston is driven to move leftwards, the first distributing groove on the piston is communicated with the copper sleeve and the oil suction hole on the cylinder body, and oil is sucked into the first high-low pressure cavity; the first roller support assembly rotates and drives the transmission shaft to synchronously rotate and move rightwards through the spline, the movement is transmitted to the third roller support assembly, and the third roller support assembly moves from the highest point of the left cam to the lowest point to drive the left concentric ring to move rightwards; the second roller bracket component transmits the motion to the fourth roller bracket component through a spline on the piston to drive the piston to move leftwards, the volume in the second high-low pressure cavity is reduced, and oil is discharged from the oil outlet through a second distributing groove on the piston; along with the rotary motion of the roller assembly, the first distributing groove and the second distributing groove are periodically changed with the oil suction holes and the oil discharge holes on the concentric rings, so that the pumping oil discharge of the roller type inertial force balancing unit is realized;
The left end cover is connected with an external oil way, and hydraulic oil enters the pump shell through four waist-shaped holes on the left end cover;
The left end cover is fixed on the left side surface of the pump shell through a bolt, and the right end cover is fixedly connected with the right end surface of the pump shell through a bolt; the left end cover, the right end cover and the pump shell are sealed by sealing rings; the cylinder body is fixedly connected to the right end face of the pump shell through bolts, and the cylinder body is sealed with the pump shell through a sealing ring.
2. The roller type force balance unit pump of claim 1, wherein: the positions of the oil suction and discharge holes on the copper bush are completely consistent with those of the oil suction and discharge holes on the cylinder body, and the outer circle of the copper bush is fixed with the inner circle of the cylinder body in an interference fit mode.
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| CN201910099225.XA CN111502951B (en) | 2019-01-31 | 2019-01-31 | Roller type force balance unit pump |
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| CN201910099225.XA CN111502951B (en) | 2019-01-31 | 2019-01-31 | Roller type force balance unit pump |
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| CN112610438A (en) * | 2020-11-23 | 2021-04-06 | 河南航天液压气动技术有限公司 | Piston pump |
| CN114645847B (en) * | 2022-05-19 | 2022-08-05 | 浙大城市学院 | Two-dimensional motor piston pump |
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