CN220452124U - Impeller supercharging sloping cam type axial plunger double pump - Google Patents
Impeller supercharging sloping cam type axial plunger double pump Download PDFInfo
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- CN220452124U CN220452124U CN202321880824.3U CN202321880824U CN220452124U CN 220452124 U CN220452124 U CN 220452124U CN 202321880824 U CN202321880824 U CN 202321880824U CN 220452124 U CN220452124 U CN 220452124U
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- pump
- impeller
- oil
- cavity
- transmission shaft
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 19
- 230000005540 biological transmission Effects 0.000 claims abstract description 12
- 230000009977 dual effect Effects 0.000 claims description 7
- 238000011010 flushing procedure Methods 0.000 claims description 5
- 238000001816 cooling Methods 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 2
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 238000007599 discharging Methods 0.000 description 3
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Abstract
The utility model discloses an impeller supercharging swash plate type axial plunger double pump, which is provided with a front transmission shaft, a rear transmission shaft, a shell assembly, a swash plate, a rotor assembly and an oil distribution disc part which are arranged back to back, wherein the front transmission shaft, the shell assembly, the swash plate, the rotor assembly and the oil distribution disc part are respectively connected with an outer intermediate body into a whole to form a back to back double pump; the front pump drives the rotor assembly to rotate by the front pump-transmission shaft, and the rear pump drives the rotor assembly to rotate by the rear pump-transmission shaft; the front pump-transmission shaft is connected with the rear pump-transmission shaft through a spline connecting sleeve, so that power transmission is realized. Compared with the traditional large-displacement axial plunger pump, the impeller supercharging swash plate type axial plunger double pump has the characteristics of compact structure, high rotating speed, heavy load and large flow, lower noise, more energy conservation and longer service life.
Description
Technical Field
The utility model relates to an impeller supercharging sloping cam plate type axial plunger pump.
Background
The industrial heavy equipment has very important status in the national economy development of China, embodies the comprehensive national force of China, and relates to national economy pulse and national safety. While hydraulic systems for heavy equipment place increasing demands on their core power element, the hydraulic pump. In particular, the application requirements of axial plunger pumps driven by large displacement, heavy load and high rotating speed of a servo motor are becoming wider. The existing heavy-load large-displacement (more than 300 ml/r) axial plunger pump is difficult to meet the requirements of high rotating speed, low noise and the like due to the limitation of the structural volume.
Disclosure of Invention
The utility model aims to provide an impeller supercharging swashplate type axial plunger double pump with high rotating speed, heavy load, large flow and low noise.
The technical scheme of the utility model is as follows:
an impeller supercharging swashplate type axial plunger double pump is characterized in that: the front and rear double pumps are respectively connected with the outer intermediate body into a whole to form a front and rear double pump which is arranged back to back; the front pump drives the rotor assembly to rotate by the front pump-transmission shaft, and the rear pump drives the rotor assembly to rotate by the rear pump-transmission shaft; the front pump-transmission shaft is connected with the rear pump-transmission shaft through a spline connecting sleeve, so that power transmission is realized.
The outer middle body is provided with a public oil inlet, a front oil outlet and a rear oil outlet; the two oil outlets can be combined to realize large-displacement oil supply, and also can independently form two hydraulic circuits.
The outer intermediate body is provided with an oil suction flow passage and an oil pressing flow passage of the front pump, and is provided with an impeller cavity and an impeller pressurizing cavity, the oil suction flow passage is communicated with the impeller pressurizing cavity, and the oil pressing flow passage is communicated with an oil outlet of the front pump; an impeller is arranged in the impeller cavity; the inner intermediate body is arranged in the outer intermediate body, the inner intermediate body is provided with an oil suction flow passage and an oil pressing flow passage of the rear pump, the oil suction flow passage is communicated with an impeller pressurizing cavity of the outer intermediate body, and the oil pressing flow passage is communicated with an oil outlet of the rear pump of the outer intermediate body.
The outer intermediate impeller cavity is internally provided with a semi-open impeller which is arranged on the external diameter of a spline of the spline connecting sleeve, oil liquid of a common oil inlet on the outer intermediate is pressurized through the impeller, and is filled into an impeller pressurizing cavity of the outer intermediate, and the pressurized oil enters respective oil suction cavity flow channels of the front pump and the rear pump respectively, so that pressurizing oil supply of the double pumps is realized, and the rotating speed is improved.
The inner intermediate body and the outer intermediate body are provided with a front channel and a rear channel which are respectively used for flushing and cooling the inner parts of the front side pump and the rear side pump from the impeller pressurizing cavity through the throttle holes so as to lubricate and cool the parts with high rotation speed.
The shell components of the front pump and the rear pump are identical in structure and comprise: a pulling rod is arranged in a transverse hole in the middle of the variable piston and is positioned and fixed through a set screw; the ball head at the lower end of the pulling rod is inserted into the hole at the upper end of the sloping cam plate; the large end of the variable piston is arranged in the upper cavity of the shell and forms a large piston cavity with the stop block, and the axis of the large piston cavity is parallel to the axis of the transmission shaft of the plunger pump; the small end of the variable piston is inserted into a small end flange hole to form a small piston cavity, and the small end flange is arranged in a corresponding hole on the upper side of the shell through a screw; the large end flange is arranged on the upper side surface of the shell through screws; the small piston cavity is communicated with the oil outlet, the control valve controls the large piston cavity to be communicated with the oil outlet so as to realize the left-right displacement of the variable piston, the ball head of the pulling rod on the variable piston drives the sloping cam plate to change the inclination angle alpha, thereby changing the stroke of the plunger, namely changing the volume of the plunger cavity, and further realizing the change of the output flow of the front pump and the rear pump.
In the front pump and the rear pump shell component, a control valve is arranged at the upper part of the shell and is a power valve; the push rod is arranged in the push rod, the cavity at the lower end of the push rod is communicated with the small piston cavity, and the push rod feeds back the pressure and the variable piston displacement (namely the inclination angle alpha of the swash plate, namely the output flow change) to the control valve so as to realize the power control of the front pump and the rear pump.
Besides the control valve (power valve), the front pump and the rear pump can also be provided with a flow valve, a pressure valve and other combined valves so as to realize various control modes of the front pump and the rear pump.
The inner intermediate body realizes circumferential positioning in the outer intermediate body through the cylindrical pin, and realizes axial positioning through the circlip for the hole.
The utility model has front and back two groups of back-to-back transmission shafts, shell components, swash plate, rotor components, oil distribution disc and other parts which are respectively connected with an outer intermediate body into a whole. The high-speed impeller has a common oil inlet, two oil outlets, an oil inlet impeller supercharging function and an internal circulation flushing cooling function, and can realize high rotation speed (more than or equal to 2000 r/min). The combination of a large displacement pump into two small displacement pumps (such as a 500ml/r displacement pump is realized by a double pump consisting of two 250ml/r displacement pumps and a 360ml/r displacement pump is realized by a double pump consisting of two 180ml/r displacement pumps) can meet the requirements of a heavy equipment hydraulic system on a large displacement, heavy load, high rotating speed and lower noise axial plunger pump.
Compared with the traditional large-displacement axial plunger pump, the impeller supercharging swash plate type axial plunger double pump has the characteristics of compact structure, high rotating speed, heavy load and large flow, lower noise, more energy conservation and longer service life.
Drawings
The utility model is further described below with reference to the drawings and examples.
Fig. 1 is an outline view of an impeller pressurizing swash plate type axial plunger double pump according to the present utility model.
Fig. 2 is a block diagram of an impeller pressurized swash plate type axial plunger double pump according to the present utility model.
Fig. 3 is a section A-A of fig. 2.
Fig. 4 is an exploded view of the major components of the impeller pressurized swash plate type axial plunger dual pump of the present utility model.
Description of the embodiments
The front pump consists of a front pump-shaft cover 1, a front pump-transmission shaft 2, a shell component 3, a swash plate seat 4, a swash plate 5, a thrust plate 6, a rotor component 7, a front pump-oil distribution disc 8, an outer intermediate 9, a large bearing 16, a small bearing 17 and the like; the rear pump consists of a rear pump-shaft cover 15, a rear pump-transmission shaft 14, a shell assembly 3, a swash plate seat 4, a swash plate 5, a thrust plate 6, a rotor assembly 7, a rear pump-oil distribution disc 13, an inner intermediate body 12, a large bearing 16, a small bearing 17, a cylindrical pin 18, a hole elastic retainer ring 19 and the like; the middle part is provided with a spline connecting sleeve 10 and an impeller 11. The rotor assembly 7 is composed of a plunger 701, a return disc 702, a spherical hinge 703, a spring 704, a gasket 705 and a cylinder 706, wherein the plunger 701 and the cylinder 706 form sealed plunger cavities L3 and L4, and oil suction is performed when the volume of the plunger is increased, and oil discharge is performed when the volume is reduced.
The impeller supercharging swash plate type axial plunger double pump is formed by connecting a front pump and a rear pump which are arranged back to back in series, and the shell is formed by connecting a shell component 3 of the front pump, a shell component 3 of the rear pump which is arranged back to back and an outer intermediate 9 through four screws respectively. Has a common oil inlet S shared by the front pump and the rear pump, and a front pump oil outlet B1 and a rear pump oil outlet B2, which are positioned on an outer intermediate body 9 in the middle of the double pumps.
The inner intermediate body 12 of the rear pump is arranged in the outer intermediate body 9, the inner intermediate body 12 realizes circumferential positioning in the outer intermediate body 9 through a cylindrical pin 18, and axial positioning is realized through a circlip 19 for holes. The oil outlet flow passage L8 of the inner intermediate body 12 is connected with the oil outlet B2 of the outer intermediate body 9, and the oil suction flow passage L7 of the inner intermediate body 12 is connected with the impeller pressurizing cavity L0 of the outer intermediate body 9.
The external power source motor (or engine) drives the front pump rotor assembly 7 to rotate through the front pump-transmission shaft 2, and simultaneously the front pump-transmission shaft 2 drives the rear pump-transmission shaft 14 and the rear pump rotor assembly 7 to rotate through the spline connecting sleeve 10, so that power transmission is realized.
The power source drives the double-pump transmission shaft to run at a high speed, oil enters the common oil inlet S from an external oil tank, an impeller 11 is mounted on a spline connecting sleeve 10 in the middle of the double pump, the impeller 11 centrifugally rotates the oil in the common oil inlet S, and the oil is thrown into an impeller pressurizing cavity L0 through an impeller cavity L9 to realize the pressurizing of the oil entering the plunger pump, and the pressure is usually 2-3 bar.
The pressurized oil in the impeller pressurizing chamber L0 is respectively pressed into the oil suction side plunger chamber L3 of the front pump rotor assembly 7 and the oil suction side plunger chamber L4 of the rear pump rotor assembly 7 through the oil suction flow passage L1 of the front pump-oil distribution disc 8 and the oil suction flow passage L2 of the rear pump-oil distribution disc 13. When the front pump plunger and the rear pump plunger rotate to the oil discharging side, oil in the plunger cavity passes through the oil discharging flow passage L5 of the front pump-oil distribution disc 8 and the oil discharging flow passage L6 of the rear pump-oil distribution disc 13 and respectively enters the oil outlet B1 of the front pump and the oil outlet B2 of the rear pump, so that the oil supply of the plunger double pump to the hydraulic system is realized.
Throttle channels L10 and L11 for flushing and cooling internal parts of the left pump and the right pump are respectively designed in the impeller pressurizing cavity L0, and oil pressure in the impeller pressurizing cavity provides flushing oil for the inner cavity of the double pump through the channels L10 and L11, so that the internal parts running at high rotation speed are well lubricated and cooled.
The two back-to-back front and rear pump housing assemblies 3 are respectively composed of a small end flange 301, a return spring 302, a spring seat 303, a housing 304, a variable piston 305, a set screw 306, a stop 307, a large end flange 308, a pulling rod 309, a push rod 310, a control valve 311 and the like.
In the front pump and rear pump shell assembly, a pulling rod 309 is installed in a transverse hole in the middle of a variable piston 305, and is positioned and fixed through a set screw 306. The ball head at the lower end of the pulling rod 309 is inserted into the hole at the upper end of the swash plate 5. The large end of the variable piston 305 is arranged in the upper cavity of the shell 304 and forms a large piston cavity with the stop block 307, and the axis of the large piston cavity is parallel to the axis of the transmission shaft of the plunger pump; the small end of the variable piston 305 is inserted into a hole of the small end flange 301 to form a small piston cavity, and the small end flange 301 is installed in a corresponding hole on the upper side of the shell 304 through screws. The large end flange 308 is mounted to the upper side of the housing 304 by screws. The small piston cavity is communicated with the oil outlet, the control valve 311 controls the large piston cavity to be communicated with the oil outlet so as to realize the left and right displacement of the variable piston 305, the ball head of the pulling rod 309 on the variable piston 305 drives the sloping cam plate 5 to change the inclination angle alpha, thereby changing the stroke of the plunger, namely changing the volume of the plunger cavity, and realizing the change of the output flow of the front pump and the rear pump.
In the front pump and rear pump housing assembly, a power valve 311 is arranged at the upper part of a housing 304, a push rod 310 is arranged in a push rod 309, a cavity at the lower end of the push rod 310 is communicated with a small piston cavity, and the push rod 310 feeds back pressure and displacement of a variable piston 305 (namely, inclination angle alpha of a swash plate, namely, output flow change) to the power valve 311 so as to realize power control of the front pump and the rear pump. The front pump and the rear pump can be provided with a flow valve, a pressure valve and other combined valves besides the power valve 311 so as to realize various control modes of the front pump and the rear pump.
The front pump and the rear pump can be used as two independent hydraulic power sources in the hydraulic system and can also be combined into a power source.
The foregoing has shown and described the basic principles, principal features and advantages of the utility model. It will be understood by those skilled in the art that the present utility model is not limited by the foregoing examples, which are provided by way of illustration of the principles of the present utility model, and that various changes and modifications may be made therein without departing from the spirit and scope of the utility model as defined in the appended claims. The scope of the utility model is defined by the appended claims and equivalents thereof.
Claims (7)
1. An impeller supercharging swashplate type axial plunger double pump is characterized in that: the front pump and the rear pump are respectively connected with the outer intermediate body into a whole to form a front pump and a rear pump which are arranged back to back; the front pump drives the rotor assembly to rotate by the front pump-transmission shaft, and the rear pump drives the rotor assembly to rotate by the rear pump-transmission shaft; the front pump-transmission shaft is connected with the rear pump-transmission shaft through a spline connecting sleeve, so that power transmission is realized.
2. The impeller pressurized swash plate type axial plunger dual pump according to claim 1, characterized in that: the outer middle body is provided with a public oil inlet, a front oil outlet and a rear oil outlet; the two oil outlets are converged to realize large-displacement oil supply or independently form two hydraulic circuits.
3. The impeller pressurized swash plate type axial plunger dual pump according to claim 1, characterized in that: the outer intermediate body is provided with an oil suction flow passage and an oil pressing flow passage of the front pump, and is provided with an impeller cavity and an impeller pressurizing cavity, the oil suction flow passage is communicated with the impeller pressurizing cavity, and the oil pressing flow passage is communicated with an oil outlet of the front pump; an impeller is arranged in the impeller cavity; the inner intermediate body is arranged in the outer intermediate body, the inner intermediate body is provided with an oil suction flow passage and an oil pressing flow passage of the rear pump, the oil suction flow passage is communicated with an impeller pressurizing cavity of the outer intermediate body, and the oil pressing flow passage is communicated with an oil outlet of the rear pump of the outer intermediate body.
4. The impeller pressurized swash plate type axial plunger dual pump according to claim 2, characterized in that: the outer intermediate impeller cavity is internally provided with a semi-open impeller which is arranged on the external diameter of a spline of the spline connecting sleeve, oil liquid of a common oil inlet on the outer intermediate is pressurized through the impeller, and is filled into an impeller pressurizing cavity of the outer intermediate, and the pressurized oil enters respective oil suction cavity flow channels of the front pump and the rear pump respectively, so that pressurizing oil supply of the double pumps is realized, and the rotating speed is improved.
5. The impeller pressurized swash plate type axial plunger dual pump according to claim 3, wherein: the inner intermediate body and the outer intermediate body are provided with a front channel and a rear channel which are respectively used for flushing and cooling the inner parts of the front side pump and the rear side pump from the impeller pressurizing cavity through the throttle holes so as to lubricate and cool the parts with high rotation speed.
6. The impeller pressurized swash plate type axial plunger dual pump according to claim 1, characterized in that: the shell components of the front pump and the rear pump are identical in structure and comprise: a pulling rod (309) is arranged in a middle transverse hole of the variable piston (305) and is positioned and fixed through a set screw (306); the ball head at the lower end of the pulling rod (309) is inserted into a hole at the upper end of the sloping cam plate (5); the large end of the variable piston (305) is arranged in the upper cavity of the shell (304) and forms a large piston cavity with the stop block (307), and the axis of the large piston cavity is parallel to the axis of the transmission shaft of the plunger pump; the small end of the variable piston (305) is inserted into a hole of the small end flange (301) to form a small piston cavity, and the small end flange (301) is arranged in a corresponding hole on the upper side of the shell (304) through a screw; the large end flange (308) is arranged on the upper side surface of the shell (304) through screws; the small piston cavity is communicated with the oil outlet, the control valve (311) controls the large piston cavity to be communicated with the oil outlet so as to realize the left-right displacement of the variable piston (305), and the ball head of the pulling rod (309) on the variable piston (305) drives the sloping cam plate (5) to change the inclination angle alpha, so that the stroke of the plunger is changed, namely the volume of the plunger cavity is changed, and the output flow of the front pump and the rear pump is changed.
7. The impeller pressurized swash plate type axial plunger dual pump according to claim 6, characterized in that: in the front pump and rear pump shell components, a control valve (311) is arranged at the upper part of a shell (304) and is a power valve; and a push rod (310) is arranged in the pull rod (309), a cavity at the lower end of the push rod (310) is communicated with the small piston cavity, and the push rod (310) feeds back the pressure and the displacement of the variable piston (305) to a control valve (311) so as to realize the power control of the front pump and the rear pump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321880824.3U CN220452124U (en) | 2023-07-18 | 2023-07-18 | Impeller supercharging sloping cam type axial plunger double pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321880824.3U CN220452124U (en) | 2023-07-18 | 2023-07-18 | Impeller supercharging sloping cam type axial plunger double pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220452124U true CN220452124U (en) | 2024-02-06 |
Family
ID=89725314
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202321880824.3U Active CN220452124U (en) | 2023-07-18 | 2023-07-18 | Impeller supercharging sloping cam type axial plunger double pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220452124U (en) |
-
2023
- 2023-07-18 CN CN202321880824.3U patent/CN220452124U/en active Active
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