CN222457754U - Radial symmetrical double-acting internal gear pump - Google Patents
Radial symmetrical double-acting internal gear pump Download PDFInfo
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- CN222457754U CN222457754U CN202421303880.5U CN202421303880U CN222457754U CN 222457754 U CN222457754 U CN 222457754U CN 202421303880 U CN202421303880 U CN 202421303880U CN 222457754 U CN222457754 U CN 222457754U
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Abstract
The utility model relates to a radial symmetrical double-acting internal gear pump, which belongs to the technical field of internal gear pumps and comprises a front cover, a front shell, a rear shell and a rear cover, wherein a cylindrical front side mounting groove is formed in the rear end face of the front shell, a cylindrical rear side mounting groove is formed in the rear end face of the rear shell, an inner rotor and an outer rotor are arranged in the front side mounting groove and the rear side mounting groove respectively, the inner rotor is sleeved on the outer side of a transmission shaft, the outer rotor is fixed on the inner walls of the front side mounting groove and the rear side mounting groove, a crescent plate is arranged between the inner rotor and the outer rotor, a front side oil outlet cavity and a front side oil outlet cavity are respectively formed in the left side and the right side of the bottom face of the front side mounting groove, a front side oil outlet cavity and a rear side oil outlet cavity are respectively formed in the left side and the right side of the bottom face of the rear side mounting groove, the front side oil outlet cavity and the rear side oil cavity are stably communicated through an oil passing channel, and the problem that the output oil of the existing single-acting internal gear pump is not solved.
Description
Technical Field
The utility model belongs to the technical field of internal gear pumps, and particularly relates to a radial symmetrical double-acting internal gear pump.
Background
As shown in fig. 1, in the conventional internal gear pump, the internal gear pump comprises a front cover 3 and a shell 22, wherein the shell 22 is fixedly connected with a rear cover 4 through a screw 7, a sealing ring 6 is arranged on the end surfaces of the shell 22, the front cover 3 and the rear cover 4, a transmission shaft 8 is arranged at the center of the shell 22, the transmission shaft drives an inner rotor 10 to be meshed with an outer rotor 11, when the inner rotor 10 rotates along with the transmission shaft 8, two sealing working cavities are formed between the inner rotor 10 and the outer rotor 11, and the sealing cavities are eccentrically arranged on one side of the shaft. The pressure oil deflected to one side generates a single-side radial force on the transmission shaft, so that the shaft moves to one side of the sliding bearing 9, the transmission shaft is subjected to the radial force to generate deflection deformation, the bearing capacity of the bearing is weakened, the two ends of the bearing are in partial contact with the shaft, and the wearing is increased and the service life of the pump is directly influenced.
As shown in fig. 1, the pressure of the internal gear pump is increased, the machining precision of the shell 22, the inner rotor 10 and the outer rotor 11 is directly improved, and the requirements on equipment are high, so that the cost and the efficiency are reduced. Meanwhile, the single-acting internal gear pump has only one eccentric, the radial output flow non-uniformity coefficient is overlarge, the flow pressure pulsation is larger, the pressure oil is unstable, and a pressure source is formed. The hydraulic oil counteracts the wall, forms the reflection wave and transmits to pressure source department, and pulsation superposes each other and produces the standing wave that harm is bigger, and output fluid is unstable. Reducing noise of internal gear pump and reducing pulsation flow becomes urgent and product quality is continuously improved.
Disclosure of utility model
The utility model overcomes the defects of the prior art, provides a radial symmetrical double-acting internal gear pump, and solves the problem that the existing single-acting internal gear pump is unstable in oil output.
In order to achieve the above purpose, the present utility model is realized by the following technical scheme.
A radial symmetrical double-acting internal gear pump comprises a front shell and a rear shell, wherein the rear end face of the front shell is in butt joint with the front end face of the rear shell, a front cover is arranged at the front end opening of the front shell, a rear cover is arranged at the rear end opening of the rear shell, a cylindrical front side mounting groove is arranged on the rear end face of the front shell, a cylindrical rear side mounting groove is arranged on the rear end face of the rear shell, a transmission shaft is inserted into the front cover, the front shell, the rear shell and the rear cover in a transmission manner, the transmission shaft sequentially penetrates through the front side mounting groove and the rear side mounting groove, an inner rotor and an outer rotor are arranged in the front side mounting groove and the rear side mounting groove, the inner rotor is sleeved on the outer side of the transmission shaft, the outer rotor is fixed on the inner walls of the front side mounting groove and the rear side mounting groove, a crescent plate is arranged between the inner rotor and the outer rotor, a front side oil outlet cavity is arranged on the left side of the bottom surface of the front side mounting groove, a front side oil inlet cavity is arranged on the right side of the bottom surface of the front side mounting groove, a front side oil inlet cavity is arranged on the left side of the bottom surface of the rear side mounting groove, a front side oil outlet cavity is arranged on the left side of the bottom surface of the rear side mounting groove, the front side oil outlet cavity is arranged on the bottom surface of the front side of the rear side oil cavity, the front side oil outlet cavity is communicated with the rear side oil outlet channel, and the front side oil outlet channel passes through the rear side oil outlet channel.
Further, the front cover and the front shell are positioned by the positioning pin, the front shell and the rear shell are positioned by the positioning pin, and the rear shell and the rear cover are positioned by the positioning pin.
Further, the screw at the front side passes through the front cover and the front shell and is in threaded connection with the rear shell, and the screw at the rear side passes through the rear cover and the rear shell and is in threaded connection with the front shell, so that the front cover, the front shell, the rear shell and the rear cover are fixedly connected.
Further, sealing rings are arranged between the front cover and the front shell, between the front shell and the rear shell and between the rear shell and the rear cover.
Further, the axis of the transmission shaft is parallel to the axes of the front side mounting groove and the rear side mounting groove, and the axis of the front side mounting groove is located above the axis of the transmission shaft, and the axis of the rear side mounting groove is located below the axis of the transmission shaft.
Further, the axes of the front inner rotor and the rear inner rotor are coincident with the axis of the transmission shaft, the axis of the front outer rotor is coincident with the axis of the front mounting groove, and the axis of the rear outer rotor is coincident with the axis of the rear mounting groove.
Further, the crescent plates are respectively and fixedly arranged in the front side mounting groove and the rear side mounting groove, the crescent plates in the front side mounting groove are positioned above the inner rotor, the crescent plates in the rear side mounting groove are positioned below the inner rotor, and the crescent plates are respectively contacted with the external meshing teeth of the inner rotor and the internal meshing teeth of the outer rotor.
Further, an oil inlet is formed in the front cover, an oil outlet is formed in the rear cover, the front side oil inlet cavity is communicated with the oil inlet in the front cover, and the rear side oil outlet cavity is communicated with the oil outlet in the rear cover.
Further, in the front side mounting groove, the area between the crescent plate and the inner engaging teeth of the outer rotor in contact is a low-pressure transition cavity, and in the rear side mounting groove, the area between the crescent plate and the inner engaging teeth of the outer rotor in contact is a high-pressure transition cavity.
Further, the front side oil inlet cavity and the rear side oil inlet cavity are arranged in a central symmetry mode relative to the axis of the transmission shaft, and the front side oil outlet cavity and the rear side oil outlet cavity are arranged in a central symmetry mode relative to the axis of the transmission shaft.
Compared with the prior art, the utility model has the following beneficial effects:
According to the radial symmetrical double-acting internal gear pump, through improving the structural design, the fluid motion path is changed, the pressure liquid flow fluctuation tends to be stable, the adaptability to loads is improved, the noise is improved, the performance test of the internal gear pump is improved, the production efficiency is high, and the increase of enterprise benefits is promoted.
Drawings
The utility model is described in further detail below with reference to the accompanying drawings:
FIG. 1 is a schematic view of a conventional internal gear pump;
FIG. 2 is a schematic overall construction of the present utility model;
FIG. 3 is a cross-sectional view C-C of FIG. 2, with the pink area of the water showing the oil within the front oil outlet chamber and the blue area showing the area within the front oil inlet chamber;
FIG. 4 is a cross-sectional view D-D of FIG. 2, showing the pink area of the oil within the rear oil inlet chamber and the red area of the oil within the rear oil outlet chamber;
FIG. 5 is a schematic view of the relative positions of the front side oil inlet chamber, the front side oil outlet chamber, the rear side oil inlet chamber, the rear side oil outlet chamber, and the oil passage;
FIG. 6 is a schematic view of the positions of the inner rotor, outer rotor, and crescent plate on the front and rear sides relative to the drive shaft;
Wherein 1 is the front shell, 2 is the back shell, 3 is the front cover, 4 is the back cover, 5 is the locating pin, 6 is the sealing washer, 7 is the screw, 8 is the transmission shaft, 9 is slide bearing, 10 is the inner rotor, 11 is the outer rotor, 12 is the crescent moon plate, 13 is the oil inlet, 14 is the oil-out, 15 is the front side oil pocket, 16 is the front side oil pocket, 17 is low pressure transition chamber, 18 is the rear side oil pocket, 19 is the rear side oil pocket, 20 is high pressure transition chamber, 21 is the oil passage.
Detailed Description
In order to make the technical problems, technical schemes and beneficial effects to be solved more clear, the utility model is further described in detail by combining the embodiments and the drawings. 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 utility model. The following describes the technical scheme of the present utility model in detail with reference to examples and drawings, but the scope of protection is not limited thereto.
As shown in fig. 2-6, the utility model provides a radial symmetrical double-acting internal gear pump, which comprises a front cover 3, a rear cover 4, a front shell 1 and a rear shell 2, wherein the rear end surface of the front shell 1 is in butt joint with the front end surface of the rear shell 2, the front cover 3 is arranged at the front end opening of the front shell 1, and the rear cover 4 is arranged at the rear end opening of the rear shell 2. The front cover 3 and the front shell 1 are positioned by the positioning pin 5, the front shell 1 and the rear shell 2 are positioned by the positioning pin 5, and the rear shell 2 and the rear cover 4 are positioned by the positioning pin 5. The screw 7 at the front side passes through the front cover 3 and the front shell 1 and is in threaded connection with the rear shell 2, and the screw 7 at the rear side passes through the rear cover 4 and the rear shell 2 and is in threaded connection with the front shell 1, so that the front cover 3, the front shell 1, the rear shell 2 and the rear cover 4 are fixedly connected. Sealing rings 6 are arranged between the front cover 3 and the front shell 1, between the front shell 1 and the rear shell 2 and between the rear shell 2 and the rear cover 4, and the sealing performance of the joint is ensured through the sealing rings 6.
A cylindrical front side mounting groove is provided on the rear end face of the front housing 1, and a cylindrical rear side mounting groove is provided on the rear end face of the rear housing 2. The front cover 3, the front shell 1, the rear shell 2 and the rear cover 4 are internally connected with a transmission shaft 8 in a transmission manner, the transmission shaft 8 sequentially penetrates through the front side mounting groove and the rear side mounting groove, the axis of the transmission shaft 8 is parallel to the axes of the front side mounting groove and the rear side mounting groove, the axis of the front side mounting groove is positioned above the axis of the transmission shaft 8, and the axis of the rear side mounting groove is positioned below the axis of the transmission shaft 8.
Sliding bearings 9 are provided between the outer side surface of the transmission shaft 8 and the inner wall of the front housing 1, between the outer side surface of the transmission shaft 8 and the inner wall of the rear housing 2, and between the outer side surface of the transmission shaft 8 and the rear cover 4.
An inner rotor 10 is arranged in the front side mounting groove, the inner rotor 10 is sleeved on the outer side of the transmission shaft 8, the axis of the inner rotor 10 coincides with the axis of the transmission shaft 8, the number of external meshing teeth on the inner rotor 10 is 10, and the inner rotor 10 is matched with the transmission shaft 8 through keys, so that the transmission shaft 8 drives the inner rotor 10 to rotate. An outer rotor 11 is fixedly arranged on the inner wall of the front side mounting groove, the axis of the outer rotor 11 is coincident with the axis of the front side mounting groove, and the number of external meshing teeth on the outer rotor 11 is 13. A crescent plate 12 is arranged between the inner rotor 10 and the outer rotor 11, the crescent plate 12 is positioned above the inner rotor 10, the crescent plate 12 is fixedly arranged in the front side mounting groove, and the crescent plate 12 is respectively contacted with the external meshing teeth of the inner rotor 10 and the internal meshing teeth of the outer rotor 11.
An inner rotor 10 is arranged in the rear side mounting groove, the inner rotor 10 is sleeved on the outer side of the transmission shaft 8, the axis of the inner rotor 10 coincides with the axis of the transmission shaft 8, the number of external meshing teeth on the inner rotor 10 is 10, and the inner rotor 10 is matched with the transmission shaft 8 through keys, so that the transmission shaft 8 drives the inner rotor 10 to rotate. An outer rotor 11 is fixedly arranged on the inner wall of the rear side mounting groove, the axis of the outer rotor 11 is coincident with the axis of the rear side mounting groove, and the number of external meshing teeth on the outer rotor 11 is 13. A crescent plate 12 is arranged between the inner rotor 10 and the outer rotor 11, the crescent plate 12 is positioned below the inner rotor 10, the crescent plate 12 is fixedly arranged inside the rear side mounting groove, and the crescent plate 12 is respectively contacted with the external meshing teeth of the inner rotor 10 and the internal meshing teeth of the outer rotor 11.
An oil inlet 13 is arranged on the front cover 3, and an oil outlet 14 is arranged on the rear cover 4.
A front oil outlet cavity 16 is arranged on the left side of the bottom surface of the front mounting groove, a front oil inlet cavity 15 is arranged on the right side of the bottom surface of the front mounting groove, the front oil inlet cavity 15 and the front oil outlet cavity 16 are respectively positioned at two ends of the front crescent plate 12, and the front oil inlet cavity 15 is communicated with the oil inlet 13 on the front cover 3. In the front mounting groove, the area between the crescent plate 12 and the tooth of the outer rotor 11 in contact is a low-pressure transition chamber 17.
A front oil inlet cavity 15 is arranged on the left side of the bottom surface of the rear mounting groove, a rear oil outlet cavity 19 is arranged on the right side of the bottom surface of the rear mounting groove, the rear oil inlet cavity 18 and the rear oil outlet cavity 19 are respectively positioned at two ends of the rear crescent plate 12, and the rear oil outlet cavity 19 is communicated with the oil outlet 14 on the rear cover 4. In the rear mounting groove, the area between the crescent plate 12 and the inner tooth of the outer rotor 11 in contact is a high-pressure transition chamber 20.
An oil passage 21 is provided in the rear housing 2, the axis of the oil passage 21 is parallel to the axis of the drive shaft 8, and the front oil outlet chamber 16 and the rear oil outlet chamber 18 are communicated through the oil passage 21.
The front side oil intake chamber 15 and the rear side oil intake chamber 18 are arranged centrally with respect to the axis of the drive shaft 8, and the front side oil discharge chamber 16 and the rear side oil discharge chamber 19 are arranged centrally with respect to the axis of the drive shaft 8.
The working principle of the utility model is as follows:
When the rotating shaft rotates, the front inner rotor 10, the rear inner rotor 11 and the crescent plate 12 are driven to rotate together, oil is sucked from the oil inlet 13 and the front oil inlet cavity 15 and discharged from the front oil outlet cavity 16, the oil discharged from the front oil outlet cavity 16 enters the rear oil inlet cavity 18 through the oil passing channel 21, and the rear inner rotor 10, the outer rotor 11 and the crescent plate 12 are matched with each other to discharge the oil outwards from the rear oil outlet cavity 19 and the oil outlet 14.
The front oil inlet cavity 15, the front oil outlet cavity 16 and the low-pressure transition cavity 17 are arranged in a central symmetry mode relative to the axis of the transmission shaft 8, and the rear oil inlet cavity 18, the rear oil outlet cavity 19 and the height transition cavity are arranged in a central symmetry mode. More than half of the oil in the front oil inlet cavity 15 and the front oil outlet cavity 16 are located above the axis of the transmission shaft 8, so that the oil has a downward component force on the transmission shaft 8, and the transmission shaft 8 has a downward movement tendency. More than half of the oil in the rear oil inlet cavity 18 and the rear oil outlet cavity 19 are positioned below the axis of the transmission shaft 8, so that the oil has an upward component force on the transmission shaft 8, and the transmission shaft 8 has a tendency to move upwards. In the whole, the upper component force and the lower component force are equal in magnitude and opposite in direction, and the external resultant force is zero. The transmission shaft 8 is stressed uniformly along the circumferential direction, and the problems of load capacity reduction and local abrasion caused by the inclination of the transmission shaft 8 in the bearing are solved.
Each time the inner rotor 10 rotates for one circle, the oil suction and discharge cycle is completed, and each time the inner rotor 10 rotates for one circle, the oil suction and discharge cycle is completed for two times, the oil suction and discharge cycle is completed, and the oil suction and discharge cycle is completed. The oil in the oil tank enters the front side oil inlet cavity 15 in the front shell 1 through the front cover 3, passes through the low-pressure transition cavity 17, is finally distributed from the front side oil outlet cavity 16, and the front side inner rotor 10 rotates once to finish oil absorption and oil discharge. Similarly, the inner rotor 10 at the rear side rotates once to absorb and distribute oil. In order to reform the transmission shaft 8 to rotate for one circle to complete oil suction and discharge circulation, the front oil inlet cavity 15, the front oil outlet cavity 16, the rear oil inlet cavity 18 and the rear oil outlet cavity 19 are designed to be of a structure which is symmetrical relative to the center of the axis of the transmission shaft 8, then the front oil outlet cavity 16 and the rear oil inlet cavity 18 are communicated through an oil passage 21, oil flowing out of the front oil outlet cavity 16 enters the rear oil inlet cavity 18, four cavities are paired in pairs, the number of the high-pressure transition cavity 20 and the low-pressure transition cavity 17 is equal and even, and the oil sequentially passes through the front oil inlet cavity 15, the front oil outlet cavity 16, the rear oil inlet cavity 18 and the rear oil outlet cavity 19 along the flowing direction, and the transmission shaft 8 rotates for one circle to complete front and rear oil suction and discharge circulation, so that the double-acting oil pump can be defined as a double-acting oil pump, the flow uniformity of the double-acting oil pump is good, and the radial hydraulic pressure born by the rotor body is basically balanced.
In the method for improving the pressure of the oil pump, the machining precision of a workpiece is improved, the pressure p is improved once, the front pump pressure is p/2, the rear pump pressure is improved from p/2 to p, in a specific implementation mode, the front shell 1 and the rear shell 2 are provided with an oil passing channel 21 which is connected with a front oil outlet cavity 16 and a rear oil outlet cavity 18, in the process that the inner rotor 10 is meshed with the outer rotor 11, initial pressure oil p/2 is formed at the front oil outlet cavity 16 of the front shell 1, and flows into the rear oil outlet cavity 18 of the rear shell 2 through the oil channel 21, oil in the rear pump p/2 is pressurized again to p, and the pressure oil p flows out of the oil pump from the rear oil outlet cavity 19. The precision of the part is determined by the pressure difference, and compared with the primary lifting pressure p, the secondary lifting pressure has obviously reduced requirement on the precision of the part, and the processing difficulty of the part is obviously reduced.
The volume of the oil inlet cavity is changed from small to large, the volume of the oil outlet cavity is changed from large to small, an oil suction pressure oil circulation is completed, the change of the radial speed and acceleration of oil in the oil cavity change area is as small as possible, the radial acceleration is infinite due to the abrupt change of the radial speed, a hard flushing is formed, the oil has a certain compressibility, energy is stored when the oil is pressurized, the energy is released when the oil is depressurized, and the pressure gradient is a noise source. The transmission shaft 8 rotates, the periodical pressure pulsation is realized, and the even-numbered cavity flow pressure pulsation is low depending on the number and arrangement positions of the high-low oil cavities at the instant position.
The oil in the oil outlet cavity generates tiny vibration, reacts on the wall to form reflected waves, and interacts with a vibration source to generate standing waves with greater harm. After the oil passing channel 21 is used for communicating oil, the oil in the four oil cavities which are arranged in a central symmetry way is communicated with each other, reflected waves are mutually counteracted and absorbed, no wave form is generated to the outside, and pulsation of output oil is reduced. Meanwhile, the transmission shaft 8 is good in lubrication, uniform in load distribution, stable in running of the inner rotor and the outer rotor 11, greatly improved in noise reduction effect and more reliable in work.
It will be evident to those skilled in the art that the utility model is not limited to the details of the foregoing illustrative embodiments, and that the present utility model may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive, the scope of the utility model being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Claims (10)
1. A radial symmetrical double-acting internal gear pump is characterized by comprising a front shell (1) and a rear shell (2), wherein the rear end face of the front shell (1) is in butt joint with the front end face of the rear shell (2), a front cover (3) is arranged at the front end opening of the front shell (1), a rear cover (4) is arranged at the rear end opening of the rear shell (2), a cylindrical front side mounting groove is arranged on the rear end face of the front shell (1), a cylindrical rear side mounting groove is arranged on the rear end face of the rear shell (2), a transmission shaft (8) is inserted in the front cover (3), the front shell (1), the rear shell (2) and the rear cover (4), the transmission shaft (8) sequentially penetrates through the front side mounting groove and the rear side mounting groove, an inner rotor (10) and an outer rotor (11) are respectively arranged in the front side mounting groove and the rear side mounting groove, the inner rotor (10) is sleeved on the outer side of the transmission shaft (8), the outer rotor (11) is fixed on the inner wall of the front side mounting groove and the rear side mounting groove, a left side outer rotor (11) is arranged between the front side bottom surface (11) and a front side bottom surface (15) of a front side bottom surface (15) is arranged on the left side bottom surface (15), the right side of the bottom surface of the rear mounting groove is provided with a rear oil outlet cavity (19), the rear shell (2) is provided with an oil passing channel (21), and the front oil outlet cavity (16) is communicated with the rear oil inlet cavity (18) through the oil passing channel (21).
2. The radial symmetrical double-acting internal gear pump according to claim 1, wherein the front cover (3) and the front shell (1) are positioned by a positioning pin (5), the front shell (1) and the rear shell (2) are positioned by the positioning pin (5), and the rear shell (2) and the rear cover (4) are positioned by the positioning pin (5).
3. The radial symmetrical double-acting internal gear pump according to claim 1, wherein the screw (7) at the front side penetrates through the front cover (3) and the front shell (1) and is in threaded connection with the rear shell (2), and the screw (7) at the rear side penetrates through the rear cover (4) and the rear shell (2) and is in threaded connection with the front shell (1), so that the front cover (3), the front shell (1), the rear shell (2) and the rear cover (4) are fixedly connected.
4. The radial symmetrical double-acting internal gear pump according to claim 1, wherein sealing rings (6) are arranged between the front cover (3) and the front shell (1), between the front shell (1) and the rear shell (2) and between the rear shell (2) and the rear cover (4).
5. A radially symmetrical double-acting internal gear pump according to claim 1, characterized in that the axis of the drive shaft (8) is parallel to the axes of the front and rear mounting grooves, and the axis of the front mounting groove is located above the axis of the drive shaft (8) and the axis of the rear mounting groove is located below the axis of the drive shaft (8).
6. A radial symmetrical double-acting internal gear pump according to claim 5, wherein the axes of the front and rear inner rotors (10) are coincident with the axis of the drive shaft (8), the axis of the front outer rotor (11) is coincident with the axis of the front mounting groove, and the axis of the rear outer rotor (11) is coincident with the axis of the rear mounting groove.
7. The radial symmetrical double-acting internal gear pump of claim 6, wherein the crescent plates (12) are fixedly arranged in the front side mounting groove and the rear side mounting groove respectively, the crescent plates (12) in the front side mounting groove are positioned above the inner rotor (10), the crescent plates (12) in the rear side mounting groove are positioned below the inner rotor (10), and the crescent plates (12) are respectively contacted with the external meshing teeth of the inner rotor (10) and the internal meshing teeth of the outer rotor (11).
8. The radial symmetrical double-acting internal gear pump according to claim 1 is characterized in that an oil inlet (13) is formed in the front cover (3), an oil outlet (14) is formed in the rear cover (4), the front side oil inlet cavity (15) is communicated with the oil inlet (13) in the front cover (3), and the rear side oil outlet cavity (19) is communicated with the oil outlet (14) in the rear cover (4).
9. A radially symmetrical double-acting internal gear pump according to claim 1, characterized in that in the front side mounting groove the area between the crescent plate (12) and the inner toothing of the contacting outer rotor (11) is a low pressure transition chamber (17) and in the rear side mounting groove the area between the crescent plate (12) and the inner toothing of the contacting outer rotor (11) is a high pressure transition chamber (20).
10. A radially symmetrical double-acting internal gear pump according to claim 1, characterized in that the front side oil inlet chamber (15) and the rear side oil inlet chamber (18) are arranged centrally symmetrically with respect to the axis of the drive shaft (8), and the front side oil outlet chamber (16) and the rear side oil outlet chamber (19) are arranged centrally symmetrically with respect to the axis of the drive shaft (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202421303880.5U CN222457754U (en) | 2024-06-07 | 2024-06-07 | Radial symmetrical double-acting internal gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202421303880.5U CN222457754U (en) | 2024-06-07 | 2024-06-07 | Radial symmetrical double-acting internal gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN222457754U true CN222457754U (en) | 2025-02-11 |
Family
ID=94454136
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202421303880.5U Active CN222457754U (en) | 2024-06-07 | 2024-06-07 | Radial symmetrical double-acting internal gear pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN222457754U (en) |
-
2024
- 2024-06-07 CN CN202421303880.5U patent/CN222457754U/en active Active
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