CN113898325A - Pumping unit capable of realizing intermittent pumping through non-whole-cycle motion of crank without stopping - Google Patents
Pumping unit capable of realizing intermittent pumping through non-whole-cycle motion of crank without stopping Download PDFInfo
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- CN113898325A CN113898325A CN202111229704.2A CN202111229704A CN113898325A CN 113898325 A CN113898325 A CN 113898325A CN 202111229704 A CN202111229704 A CN 202111229704A CN 113898325 A CN113898325 A CN 113898325A
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- 238000005086 pumping Methods 0.000 title claims abstract description 49
- 230000033001 locomotion Effects 0.000 title claims abstract description 30
- 239000003638 chemical reducing agent Substances 0.000 claims abstract description 35
- 230000007246 mechanism Effects 0.000 claims abstract description 16
- 238000000605 extraction Methods 0.000 claims abstract description 8
- 230000009471 action Effects 0.000 claims description 4
- 239000003129 oil well Substances 0.000 abstract description 14
- 239000007788 liquid Substances 0.000 abstract description 8
- 230000005540 biological transmission Effects 0.000 abstract description 7
- 238000004804 winding Methods 0.000 description 9
- 230000005484 gravity Effects 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
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Classifications
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- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
- E21B43/121—Lifting well fluids
- E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
- E21B43/127—Adaptations of walking-beam pump systems
Abstract
A pumping unit for realizing intermittent pumping through non-whole-cycle motion of a crank without stopping relates to the technical field of oil field oil extraction equipment and comprises a motor, a speed reducer, a crank assembly, a connecting rod, a walking beam and a bracket, wherein the motor is connected with an input shaft of the speed reducer through a belt transmission mechanism, the end part of the crank assembly is arranged on an output shaft of the speed reducer and is driven by the speed reducer to rotate, the middle part of the walking beam is hinged to the top end of the bracket, and the upper end and the lower end of the connecting rod are respectively hinged to the tail part of the walking beam and the crank assembly; the crank assembly comprises a gear carrier, a conventional gear train, an inter-extraction gear train, a crank main body and a switching mechanism, wherein the gear carrier, the conventional gear train and the inter-extraction gear train are all arranged in a round hole in the center of the crank main body. The invention can make the crank swing with small amplitude through a special mechanism, and the small amplitude swing is equivalent to greatly reducing the stroke of the oil pumping unit, thereby greatly reducing the oil pumping speed, leading the oil pumping speed to be greatly smaller than the seepage speed of underground liquid, and avoiding the dry pumping of the oil well pump.
Description
Technical Field
The invention belongs to the technical field of oil extraction equipment in oil fields, and particularly relates to an oil pumping unit which realizes intermittent pumping through non-whole-cycle motion of a crank without stopping.
Background
The drawing process is as follows: in the oil field production, along with the continuous exploitation of oil well, the seepage speed of liquid in the pit can constantly reduce, and when liquid seepage speed in the pit was less than the oil pumping speed of beam-pumping unit, just need make oil-well pump stop work in the pit, waits to restart the oil-well pump after the liquid accumulation in the pit, so relapse, makes liquid measure in the pit and the oil pumping speed phase-match of beam-pumping unit, prevents to appear "dry pumping" phenomenon and damages the oil-well pump.
In the prior art, because the stroke of the pumping unit cannot be adjusted in a large range, the underground oil well pump can only be stopped by turning off the pumping unit, but the pumping unit is completely stopped, so that liquid in an oil pipe near a well head is in a completely static state and is lack of flowing or stirring, and the phenomenon of freezing and blocking the well head in winter is easily caused in a northern severe cold area. Therefore, it is necessary to develop a new technical solution to solve the problem.
Disclosure of Invention
In order to solve the technical problems in the background technology, the invention provides an oil pumping unit which realizes intermittent pumping without stopping through non-whole-cycle motion of a crank.
The technical problem solved by the invention is realized by adopting the following technical scheme: the invention provides a pumping unit for realizing intermittent pumping through non-whole-cycle motion of a crank without stopping, which comprises a motor, a speed reducer, a crank assembly, a connecting rod, a walking beam and a bracket, wherein the motor is connected with an input shaft of the speed reducer through a belt transmission mechanism, the end part of the crank assembly is arranged on an output shaft of the speed reducer and is driven by the speed reducer to rotate, the middle part of the walking beam is hinged at the top end of the bracket, and the upper end and the lower end of the connecting rod are respectively hinged at the tail part of the walking beam and the crank assembly;
the crank assembly comprises a gear carrier, a conventional gear train, an inter-extraction gear train, a crank main body and a switching mechanism, wherein the gear carrier, the conventional gear train and the inter-extraction gear train are all arranged in a circular hole in the center of the crank main body;
the gear carrier comprises an inner gear carrier, an outer gear carrier and a wheel shaft, the inner gear carrier and the outer gear carrier are arranged in parallel, two ends of the wheel shaft are respectively and fixedly connected to the inner gear carrier and the outer gear carrier, and the inner gear carrier is fixedly connected with the speed reducer;
the conventional gear train comprises a first central gear and a first reversing gear, wherein the first reversing gear is mounted on the wheel shaft through a bearing, the first central gear is mounted on the inner side of the first reversing gear, and the inner side and the outer side of the first reversing gear are respectively meshed with the first central gear and the crank main body;
the intermittent gear train comprises a second central gear, a second reversing gear, a first unilateral gear and a second unilateral gear, wherein two gear tooth sections with different diameters are arranged and processed on the outer side of the second central gear, the gear tooth section with the smaller diameter is called an inner gear tooth section, the gear tooth section with the larger diameter is called an outer gear tooth section, and the inner gear tooth section and the outer gear tooth section are in staggered connection along the circumferential direction and cover a circumference of 360 degrees;
the second reversing gear, the first single-side gear and the second single-side gear are all mounted on the wheel shaft through bearings, the inner side and the outer side of the second reversing gear are respectively meshed with the outer gear teeth and the crank main body, the inner side of the first single-side gear is meshed with the inner gear teeth, the outer side of the second single-side gear is meshed with the crank main body, and meanwhile, the first single-side gear and the second single-side gear are meshed with each other;
the switching mechanism comprises a switching sleeve and an electromagnetic driver, the electromagnetic driver is fixedly connected to the speed reducer, the switching sleeve is sleeved on an output shaft of the speed reducer and matched with the output shaft through a spline, the switching sleeve axially reciprocates along the output shaft of the speed reducer under the action of the electromagnetic driver, and the switching sleeve is positioned between the first central gear and the output shaft of the speed reducer;
two gear rings are processed on the section of the switching sleeve between the first central gear and the second central gear, and before and after the switching sleeve moves axially, the two gear rings are meshed with the first central gear or the second central gear, so that power switching is realized.
Preferably, there is only one of the inner and outer gear tooth segments, the coverage angle of the inner and outer gear tooth segments is 180 degrees, and the projections of the inner and outer gear tooth segments on a plane perpendicular to the second central gear axis are offset to form a 360-circle circumference.
Preferably, there are two inner gear tooth sections and two outer gear tooth sections, the inner gear tooth sections and the outer gear tooth sections are alternately arranged in a staggered manner on the circumference of the second sun gear, the coverage angle of each inner gear tooth section and each outer gear tooth section is 90 degrees, and the projections of the inner gear tooth sections and the outer gear tooth sections on a plane perpendicular to the axis of the second sun gear are staggered to form a 360-degree circumference.
The invention has the beneficial effects that:
1. in the traditional oil pumping machine, a crank only can do complete and unidirectional circular motion under the driving of a speed reducer, and the crank can do small-amplitude swing through a special mechanism, and the small-amplitude swing is equivalent to the great reduction of the stroke of the oil pumping machine, so that the oil pumping speed is greatly reduced, the oil pumping speed is greatly lower than the seepage speed of underground liquid, and the dry pumping of the oil well pump is avoided. In addition, the number of the inner gear tooth sections and the outer gear tooth sections on the second central gear is increased, so that the swing amplitude of the crank can be further reduced, and due to the existence of the elongation of the sucker rod, when the swing amplitude of the crank is small enough, the underground oil well pump can completely stop working, so that the complete pumping stop of the oil well pump is realized under the condition that the oil pumping unit does not stop.
2. In the invention, the crank can be rapidly switched between a normal working state (namely, the whole-circle rotation) and a small-amplitude swinging state, and the unmanned control can be realized by automatically controlling the power on and off of the electromagnetic driver.
3. The invention can be used for transforming the traditional oil pumping unit without producing and installing a new oil pumping unit again, thereby achieving the purpose of saving equipment cost and installation cost.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a schematic structural view of the crank assembly;
FIG. 3 is a schematic view of the mounting structure of the gear carrier, the conventional gear train, the intermediate gear train and the switching mechanism on the output shaft of the speed reducer;
FIG. 4 is an enlarged view of a portion of FIG. 3 at A;
FIG. 5 is a schematic cross-sectional view of the second sun gear;
FIG. 6 is a cross-sectional view at B and C of FIG. 5 with the number of inner and outer gear tooth segments equal;
FIG. 7 is a projection of the inner and outer gear tooth segments of FIG. 5 onto a plane perpendicular to the second sun gear axis, when the number of inner and outer gear tooth segments is one;
FIG. 8 is a cross-sectional view at B and C of FIG. 5 with two inner and outer gear tooth segments;
FIG. 9 is a projection of the inner and outer gear tooth segments of FIG. 5 onto a plane perpendicular to the second sun gear axis when the number of inner and outer gear tooth segments is two;
FIG. 10 is a cross-sectional view at B and C of FIG. 5 with three inner and outer gear tooth segments;
FIG. 11 is a projection of the inner and outer gear tooth segments of FIG. 5 onto a plane perpendicular to the second sun gear axis when the number of inner and outer gear tooth segments is three;
FIG. 12 is a schematic structural view of a crank in the fourth embodiment.
In the figure: 1. the device comprises a motor, 2, a speed reducer, 3, a crank assembly, 4, a connecting rod, 5, a walking beam, 6, a bracket, 7, a crank main body, 8, a wheel shaft, 9, an inner gear section, 10, an outer wheel frame, 11, a second central gear, 12, an outer gear section, 13, a second reversing gear, 14, a first single-side gear, 15, a second single-side gear, 16, an output shaft, 17, a first reversing gear, 18, a first central gear, 19, an inner wheel frame, 20, a switching sleeve, 21, an electromagnetic driver, 22, a gear ring, 23, a balancing weight, 24, a spring, 25, a traction rope, 26, a guide wheel, 27 and a winding wheel.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
the first embodiment is as follows:
as shown in fig. 1, the present embodiment includes a motor 1, a speed reducer 2, a crank assembly 3, a connecting rod 4, a walking beam 5 and a bracket 6, the motor 1 is connected with an input shaft of the speed reducer 2 through a belt transmission mechanism, an end portion of the crank assembly 3 is mounted on an output shaft 16 of the speed reducer 2 and is driven by the speed reducer 2 to rotate, a middle portion of the walking beam 5 is hinged to a top end of the bracket 6, and upper and lower ends of the connecting rod 4 are respectively hinged to a tail portion of the walking beam 5 and the crank assembly 3. When the walking beam reciprocating swing mechanism works, power provided by the motor 1 is transmitted to the speed reducer 2 and then converted into rotary motion of the crank assembly 3, and the rotary motion of the crank assembly 3 is converted into reciprocating swing of the walking beam 5 through the connecting rod 4. The above structure is a conventional structure in the prior art, and is not described in detail herein.
The innovation of the invention is the innovation of the crank assembly 3. In the traditional oil pumping machine, a crank can only do complete and unidirectional circular motion under the driving of a speed reducer 2, but the crank can do small-amplitude swing through a special mechanism, and the small-amplitude swing is equivalent to the fact that the stroke of the oil pumping machine is greatly reduced, so that the oil pumping speed is greatly reduced, the oil pumping speed is greatly lower than the seepage speed of underground liquid, and the dry pumping of an oil well pump is avoided. In addition, the number of the inner gear section 9 and the outer gear section 12 on the second central gear 11 is increased, so that the swing amplitude of the crank can be further reduced, and due to the existence of the elongation of the sucker rod, when the swing amplitude of the crank is small enough, the underground oil well pump can completely stop working, so that the complete pumping stop of the oil well pump is realized under the condition that the oil well pump does not stop working.
As shown in fig. 2 and 3, the crank assembly 3 includes a gear carrier, a conventional gear train, an inter-gear train, a crank body 7 and a switching mechanism, wherein the gear carrier, the conventional gear train and the inter-gear train are all installed in a circular hole in the center of the crank body 7. In the above structure, the gear rack is used for mounting the gear, the conventional gear train is used for enabling the crank main body 7 to perform conventional circular motion (namely, complete circular motion) so as to ensure the normal operation of the pumping unit, the intermittent gear train is used for enabling the crank main body 7 to perform small-amplitude swing (namely, non-complete circular motion), and the switching mechanism is used for switching the crank main body 7 between the circular motion state and the swing motion state.
As shown in fig. 2 and 3, the gear carrier includes an inner gear carrier 19, an outer gear carrier 10 and a wheel axle 8, the inner gear carrier 19 and the outer gear carrier 10 are arranged in parallel, two ends of the wheel axle 8 are respectively fixedly connected to the inner gear carrier 19 and the outer gear carrier 10, and the inner gear carrier 19 is fixedly connected to the speed reducer 2. In operation, the carrier carries and the majority of the weight of the crank body 7, and therefore care must be taken to ensure its structural strength when implemented.
As shown in fig. 2 and 3, the conventional wheel train comprises a first sun gear 18 and a first reversing gear 17, wherein the first reversing gear 17 is mounted on the wheel shaft 8 through a bearing, the first sun gear 18 is mounted inside the first reversing gear 17, and the inner side and the outer side of the first reversing gear 17 are respectively meshed with the first sun gear 18 and the crank body 7. When the pumping unit normally pumps oil, the output shaft 16 of the speed reducer 2 drives the first central gear 18 to rotate, and the rotary motion of the first central gear 18 is converted into the rotary motion (namely, the whole-circle motion) of the crank main body 7 through the first reversing gear 17, so that the normal work of the pumping unit is ensured.
As shown in fig. 2 and 3, the intermittent gear train includes a second sun gear 11, a second reversing gear 13, a first single-sided gear 14 and a second single-sided gear 15, two gear tooth sections with different diameters are arranged on the outer side of the second sun gear 11, wherein the gear tooth section with the smaller diameter is called an inner gear tooth section 9, the gear tooth section with the larger diameter is called an outer gear tooth section 12, and the inner gear tooth section 9 and the outer gear tooth section 12 are staggered in the circumferential direction and cover a circumference of 360 degrees. The second reversing gear 13, the first single-sided gear 14 and the second single-sided gear 15 are all mounted on the wheel shaft 8 through bearings, the inner side and the outer side of the second reversing gear 13 are respectively meshed with the outer gear teeth and the crank body 7, the inner side of the first single-sided gear 14 is meshed with the inner gear teeth, the outer side of the second single-sided gear 15 is meshed with the crank body 7, and meanwhile, the first single-sided gear 14 and the second single-sided gear 15 are meshed with each other.
When the intermittent drawing is needed, the output shaft 16 of the speed reducer 2 drives the second central gear 11 to rotate, and because the inner gear tooth sections 9 and the outer gear tooth sections 12 on the second central gear 11 are alternately arranged in a staggered manner, the inner gear tooth sections 9 and the outer gear tooth sections 12 can only alternately participate in the transmission of power. When the external gear tooth section 12 participates in power transmission, the rotational motion of the second sun gear 11 is transmitted to the crank body 7 through the second reversing gear 13, so that the rotational motion of the second sun gear 11 is converted into the forward rotational motion of the crank body 7; when the internal gear tooth section 9 participates in the power transmission, the rotational movement of the second sun gear 11 is transmitted to the crank body 7 through the first single-sided gear 14 and the second single-sided gear 15 in order, so that the rotational movement of the second sun gear 11 is converted into the reverse rotational movement of the crank body 7. The inner gear tooth section 9 and the outer gear tooth section 12 are staggered in the circumferential direction and cover a circumference of 360 degrees, so that the forward rotation motion and the reverse rotation motion of the crank body 7 can be seamlessly engaged and switched, and the reciprocating swing of the crank body 7 is realized.
It should be noted that, in order to ensure that the gears are correctly engaged and that the inner gear section 9 and the outer gear section 12 are smoothly engaged at the moment of transmission and withdrawal, the modules of the gears, the inner gear section 9 and the outer gear section 12 must be the same.
As shown in fig. 3, the switching mechanism includes a switching sleeve 20 and an electromagnetic driver 21, the electromagnetic driver 21 is fixedly connected to the speed reducer 2, the switching sleeve 20 is sleeved on the output shaft 16 of the speed reducer 2 and is matched with the output shaft 16 through a spline, the switching sleeve 20 makes axial reciprocating motion along the output shaft 16 of the speed reducer 2 under the action of the electromagnetic driver 21, and the switching sleeve 20 is located between the first sun gear 18 and the output shaft 16 of the speed reducer 2. Two gear rings 22 are machined on the section, located between the first sun gear 18 and the second sun gear 11, of the switching sleeve 20, the switching sleeve 20 moves axially under the magnetic force of an electromagnetic driver 21 (which can be simplified as an electromagnet), and the two gear rings 22 are meshed with the first sun gear 18 or the second sun gear 11, so that power switching is achieved.
As shown in fig. 5, 6 and 7, there is only one inner gear tooth section 9 and one outer gear tooth section 12, the coverage angles of the inner gear tooth section 9 and the outer gear tooth section 12 are both 180 degrees, and the projections of the inner gear tooth section 9 and the outer gear tooth section 12 on a plane perpendicular to the axis 8 of the second central gear 11 are staggered to form a 360-circle circumference.
Example two:
the present exemplary embodiment differs from the first exemplary embodiment in that the number of internal gear tooth segments 9 and external gear tooth segments 12 differs.
As shown in fig. 5, 8 and 9, there are two inner gear tooth sections 9 and two outer gear tooth sections 12, the inner gear tooth sections 9 and the outer gear tooth sections 12 are alternately arranged on the circumference of the second central gear 11 in a staggered manner, the coverage angle of each inner gear tooth section 9 and each outer gear tooth section 12 is 90 degrees, and the projections of the inner gear tooth sections 9 and the outer gear tooth sections 12 on a plane perpendicular to the axis 8 of the second central gear 11 are staggered to form a 360-degree circumference.
Compared with the first embodiment, the present embodiment has the advantage that the amplitude of the swing of the crank body 7 is smaller, and the unnecessary wear on the plunger of the oil well pump is smaller.
Example three:
the embodiment differs from the first embodiment in the number of inner and outer gear tooth segments 9, 12.
As shown in fig. 5, 10 and 11, there are two inner gear tooth sections 9 and two outer gear tooth sections 12, the inner gear tooth sections 9 and the outer gear tooth sections 12 are alternately arranged on the circumference of the second central gear 11 in a staggered manner, the coverage angle of each inner gear tooth section 9 and each outer gear tooth section 12 is 90 degrees, and the projections of the inner gear tooth sections 9 and the outer gear tooth sections 12 on a plane perpendicular to the axis 8 of the second central gear 11 are staggered to form a 360-degree circumference.
Example four:
as shown in fig. 12, the present embodiment is different from the first embodiment in that a weight 23 with a movable position is additionally arranged in the crank body 7, the weight 23 is slidably mounted in an arc-shaped track on the crank body 7, more than one weight 23 is arranged, two adjacent weights 23 are supported by a spring 24, meanwhile, the balancing weight is connected through a traction rope 25, the traction rope 25 is connected on a winding wheel 27 after winding a guide wheel 26, the winding wheel 27 is arranged on the outer wheel frame 10 and can obtain the power of the output shaft 16 through an electromagnetic clutch, thereby winding the traction rope 25 on the winding wheel 27, and along with the winding of the traction rope 25, each balancing weight 23 gathers towards the middle, the center of gravity of the crank body 7 as a whole moves downward in fig. 12, and after the pull rope 25 is released, each weight 23 is reset under the action of the spring 24, so that the center of gravity of the crank body 7 as a whole moves upward in fig. 12. The center of gravity of the crank body 7 can be adjusted by controlling the winding wheel 27, so that different requirements on counterweight loads under different rotation states of the crank assembly are met.
It should be noted that the winding wheel 27 needs to be self-locked after rotating, and the self-locking structure can refer to the self-locking structure of the electric hoist, and is not described herein again.
Claims (3)
1. The utility model provides a through the non-stop beam-pumping unit who takes out between whole circular motion of crank, includes motor (1), speed reducer (2), crank assembly (3), connecting rod (4), walking beam (5) and support (6), its characterized in that:
the crank assembly (3) comprises a gear carrier, a conventional gear train, an inter-extraction gear train, a crank main body (7) and a switching mechanism, wherein the gear carrier, the conventional gear train and the inter-extraction gear train are all arranged in a round hole in the center of the crank main body (7);
the gear carrier comprises an inner gear carrier (19), an outer gear carrier (10) and a wheel shaft (8), wherein the inner gear carrier (19) and the outer gear carrier (10) are arranged in parallel, two ends of the wheel shaft (8) are fixedly connected to the inner gear carrier (19) and the outer gear carrier (10) respectively, and the inner gear carrier (19) is fixedly connected with the speed reducer (2);
the conventional wheel train comprises a first central gear (18) and a first reversing gear (17), wherein the first reversing gear (17) is mounted on the wheel shaft (8) through a bearing, the first central gear (18) is mounted on the inner side of the first reversing gear (17), and the inner side and the outer side of the first reversing gear (17) are respectively meshed with the first central gear (18) and the crank body (7);
the intermittent gear train comprises a second central gear (11), a second reversing gear (13), a first unilateral gear (14) and a second unilateral gear (15), wherein two gear tooth sections with different diameters are arranged on the outer side of the second central gear (11) and are respectively called an inner gear tooth section (9) and an outer gear tooth section (12), and the inner gear tooth section (9) and the outer gear tooth section (12) are in staggered connection along the circumferential direction and cover a circumference of 360 degrees;
the second reversing gear (13), the first single-side gear (14) and the second single-side gear (15) are all mounted on the wheel shaft (8) through bearings, the inner side and the outer side of the second reversing gear (13) are respectively meshed with the outer gear teeth and the crank main body (7), the inner side of the first single-side gear (14) is meshed with the inner gear teeth, the outer side of the second single-side gear (15) is meshed with the crank main body (7), and meanwhile, the first single-side gear (14) and the second single-side gear (15) are meshed with each other;
the switching mechanism comprises a switching sleeve (20) and an electromagnetic driver (21), wherein the electromagnetic driver (21) is fixedly connected to the speed reducer (2), the switching sleeve (20) is sleeved on an output shaft (16) of the speed reducer (2) and is matched with the output shaft (16) through a spline, the switching sleeve (20) axially reciprocates along the output shaft (16) of the speed reducer (2) under the action of the electromagnetic driver (21), and the switching sleeve (20) is located between the first central gear (18) and the output shaft (16) of the speed reducer (2);
two gear rings (22) are machined on the section, located between the first central gear (18) and the second central gear (11), of the switching sleeve (20), and the two gear rings (22) are meshed with the first central gear (18) or the second central gear (11) before and after the switching sleeve (20) moves axially, so that power switching is achieved.
2. The pumping unit of claim 1, wherein the pumping unit is capable of pumping oil without stopping the crank in a non-full-circle motion, and comprises: the gear wheel structure is characterized in that only one inner gear wheel section (9) and one outer gear wheel section (12) are arranged, the coverage angles of the inner gear wheel section (9) and the outer gear wheel section (12) are 180 degrees, and the projections of the inner gear wheel section (9) and the outer gear wheel section (12) on a plane perpendicular to the axis (8) of the second central gear (11) are staggered to form a 360-degree circumference.
3. The pumping unit of claim 1, wherein the pumping unit is capable of pumping oil without stopping the crank in a non-full-circle motion, and comprises: the number of the inner gear tooth sections (9) and the number of the outer gear tooth sections (12) are two, the inner gear tooth sections (9) and the outer gear tooth sections (12) are alternately arranged on the circumference of the second central gear (11) in a staggered mode, the coverage angle of each inner gear tooth section (9) and each outer gear tooth section (12) is 90 degrees, and the projections of the inner gear tooth sections (9) and the outer gear tooth sections (12) on a plane perpendicular to the axis (8) of the second central gear (11) are staggered to form a 360-degree circumference.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111229704.2A CN113898325A (en) | 2021-10-22 | 2021-10-22 | Pumping unit capable of realizing intermittent pumping through non-whole-cycle motion of crank without stopping |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111229704.2A CN113898325A (en) | 2021-10-22 | 2021-10-22 | Pumping unit capable of realizing intermittent pumping through non-whole-cycle motion of crank without stopping |
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| Publication Number | Publication Date |
|---|---|
| CN113898325A true CN113898325A (en) | 2022-01-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111229704.2A Pending CN113898325A (en) | 2021-10-22 | 2021-10-22 | Pumping unit capable of realizing intermittent pumping through non-whole-cycle motion of crank without stopping |
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