CN117703752A - Rotor pump and diesel engine - Google Patents

Abstract

The invention discloses a rotor pump and a diesel engine, which comprises a pump housing, a gear, a rotor and a balance weight, wherein the pump housing forms a structure for supporting the gear, the rotor and the balance weight; the rotor rotates along with the gear; the balancing weight is eccentrically arranged on the rotor. The rotor pump of the invention can counteract the second-order reciprocating inertial force in the running process because the rotor is eccentrically provided with the balancing weight. So that the rotor pump integrates two functions of pumping lubricating oil and balancing the second-order reciprocating inertial force of the diesel engine. Therefore, vibration isolation performance, lubrication performance, and space performance can be simultaneously achieved.

Description

Rotor pump and diesel engine

Technical Field

The invention relates to the technical field of engines, in particular to a rotor pump and a diesel engine.

Background

In order to solve the problems of poor vibration and lubrication, the diesel engine can be independently provided with a secondary balance mechanism and a rotor pump. However, the space occupied by the independent arrangement of the secondary balance mechanism and the rotor pump is large.

Therefore, how to combine vibration isolation performance, lubrication performance and space performance is a technical problem to be solved by those skilled in the art.

Disclosure of Invention

The invention provides a rotor pump and a diesel engine, which are used for considering vibration prevention performance, lubricating performance and space performance.

In order to achieve the above object, the present invention provides the following technical solutions:

in a first aspect, the present invention provides a rotor pump comprising a pump housing, a gear, a rotor and a counterweight, wherein the pump housing forms a structure supporting the gear, the rotor and the counterweight; the rotor rotates along with the gear; the balancing weight is eccentrically arranged on the rotor.

Optionally, in the rotor pump of the present invention, the pump housing forms a cavity for accommodating the rotor, the rotor is rotatably disposed in the cavity around its own axis, and the gear is disposed outside the cavity and is in driving connection with the rotor.

Optionally, in the rotor pump of the present invention, a center line of the liquid outlet and a center line of the liquid inlet of the pump housing are perpendicular to a rotation axis of the rotor.

Optionally, in the rotor pump of the present invention, the pump housing includes a first housing and a second housing, the first housing and the second housing are spliced to form the pump housing, and the liquid outlet and the liquid inlet may be formed in the first housing and/or the second housing.

Optionally, in the rotor pump of the present invention, the first housing and the second housing may be detachably connected or non-detachably connected.

Alternatively, in the rotor pump of the present invention, the number of gears and the number of rotors are two, specifically, the first gear and the first rotor are coaxially arranged on the first rotating shaft, and the second gear and the second rotor are coaxially arranged on the second rotating shaft.

Optionally, in the rotor pump of the present invention, the angular speeds of the first rotor and the second rotor are the same, and the directions are opposite.

Optionally, in the rotor pump of the present invention, the first rotor and the second rotor are identical in structure.

Optionally, in the rotor pump of the present invention, the rotor includes a rotor body and a plurality of rotor arms, the rotor arms are formed by extending the rotor body in a radial direction, and the ends of the rotor arms are in sliding contact with the wall of the housing; the balancing weight includes the balancing weight, among all rotor arms, and part rotor arm is provided with the balancing weight, and the balance is not provided with the balancing weight to make the mass central line of rotor take place the skew for the axis of rotation, the density of balancing weight is greater than the density of rotor.

Optionally, in the rotor pump of the present invention, the balancing weight further includes a weight-reducing hole, and the weight-reducing hole is disposed on a rotor arm where the balancing weight is not disposed among all the rotor arms.

Optionally, in the rotor pump of the present invention, the rotor arm provided with the balancing weight is provided with an adjusting hole, and the balancing weight is installed in the adjusting hole.

In a second aspect, the invention provides a diesel engine, comprising a cylinder, a crankshaft mechanism, an oil pan and a rotor pump, wherein the crankshaft mechanism is arranged in the cylinder, the rotor pump is positioned in the oil pan, the rotor pump is any one of the rotor pumps, and a gear of the rotor pump is in transmission connection with a crankshaft gear of the crankshaft mechanism.

According to the technical scheme, the rotor pump is provided with the balancing weight due to the fact that the rotor is eccentric, so that the rotor pump can offset second-order reciprocating inertial force in the running process. So that the rotor pump integrates two functions of pumping lubricating oil and balancing the second-order reciprocating inertial force of the diesel engine. Therefore, vibration isolation performance, lubrication performance, and space performance can be simultaneously achieved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It is apparent that the drawings in the following description are only some examples or embodiments of the present invention, and it is possible for those of ordinary skill in the art to obtain other drawings from the provided drawings without inventive effort, and to apply the present invention to other similar situations from the provided drawings. Unless otherwise apparent from the context of the language or otherwise specified, like reference numerals in the figures refer to like structures or operations.

FIG. 1 is a schematic view of a diesel engine with a secondary balance mechanism according to an embodiment of the present invention;

FIG. 2 is a schematic diagram of a secondary balance mechanism according to an embodiment of the present invention;

FIG. 3 is a schematic cross-sectional view of a secondary balance mechanism according to an embodiment of the present invention;

FIG. 4 is a schematic diagram of a secondary balance mechanism according to an embodiment of the present invention;

FIG. 5 is a schematic diagram of a rotor pump according to an embodiment of the present invention;

FIG. 6 is a schematic diagram of a diesel engine with a rotor pump according to an embodiment of the present invention;

FIG. 7 is a schematic view of another embodiment of a diesel engine with a rotor pump;

FIG. 8 is a schematic view of a third type of a diesel engine with a rotary pump according to an embodiment of the present invention;

FIG. 9 is a cross-sectional view of another section of a diesel engine with a rotor pump according to an embodiment of the present invention;

FIG. 10 is an exploded view of a rotor pump according to an embodiment of the present invention;

FIG. 11 is a cross-sectional view of a rotor pump according to an embodiment of the present invention;

FIG. 12 is a schematic diagram of a rotor pump according to an embodiment of the present invention applied to a diesel engine;

in the illustration, a 1-cylinder, a 2-crankshaft mechanism, a 3-oil pan, a 4-secondary balance mechanism and a 5-rotor pump;

21-a crankshaft gear, 22-an intermediate gear;

41-balance housing, 42-balance gear, 43-balance weight;

51-pump shell, 52-gear, 53-rotor, 54-balancing weight and 55-rotating shaft;

511-a first housing, 512-a second housing; 521-first gear, 522-second gear, 531-first rotor, 532-second rotor, 551-first shaft, 552-second shaft; 5311-rotor body, 5312-rotor arm, 5313-weight-lowering aperture.

Detailed Description

The invention is described in further detail below with reference to the drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. The described embodiments are only some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

Referring to fig. 1, fig. 1 shows a cross-sectional view of a diesel engine with a secondary balance mechanism (also called a second-order balance mechanism) installed at an angle.

The illustrated diesel engine comprises a cylinder 1, a crank mechanism 2, an oil pan 3 and a secondary balance mechanism 4, wherein the crank mechanism 2 is arranged in the cylinder 1, the oil pan 3 is arranged at the bottom of the cylinder 1, and the secondary balance mechanism 4 is arranged inside the oil pan 3 and is in transmission connection with a crank gear 21 of the crank mechanism 2. The diesel engine can balance the second-order reciprocating inertial force by arranging the second-order balancing mechanism 4, and reduce the vibration of the diesel engine caused by the existence of the second-order reciprocating inertial force.

Referring to fig. 2 and 3, the illustrated secondary balance mechanism 4 includes a balance housing 41, a balance gear 42, and a balance weight 43, wherein the balance gear 42 is rotatably disposed around its own axis within the balance housing 41, and the balance weight 43 is eccentrically disposed on the balance gear 42. The balance gears 42 are two, namely a first balance gear 42 and a second balance gear 42, the first balance gear 42 is meshed with the second balance gear 42, and one of the two balance gears is meshed with the crankshaft balance gear 42; the balancing weight 43 has two balancing weights 43, respectively, a first balancing weight 43 and a second balancing weight 43, the first balancing weight 43 being arranged on the first balancing gear 42, and the second balancing weight 43 being arranged on the second balancing gear 42.

As shown in fig. 4, the crankshaft mechanism 2 drives the first balance gear 42 to rotate through the crankshaft balance gear 42, the first balance gear 42 is meshed with the second balance gear 42, and drives the first balance weight 43 and the second balance weight 43 to rotate following the corresponding balance gears 42, during the transmission process, the crankshaft mechanism 2 rotates clockwise at the angular speed ω1, the first balance weight 43 rotates counterclockwise at the angular speed ω2, and the second balance weight 43 rotates clockwise at the angular speed ω3. The force F of the first counterweight 43 acting on the crankshaft mechanism 2 _s1 Force F of second counterweight 43 acting on crankshaft mechanism 2 _s2 Wherein F is _s1 In the vertical directionForce F _sv1 ，F _s1 Component force in horizontal direction F _sh1 ，F _s2 The component force in the vertical direction is F _sv2 ，F _s2 Component force in horizontal direction F _sv2 ；F _sv1 、F _sv2 The sum of the two and the second-order reciprocating inertial force F of the crankshaft mechanism 2 _2nd Offset, at the same time of component F in horizontal direction _sh1 、F _sh2 Which cancel each other out. It can be seen that the secondary balance mechanism 4 compensates the second-order reciprocating inertial force F of the diesel engine _2nd To dampen the vibration of the diesel engine.

The above mainly describes the scheme that the diesel engine slows down the vibration of the diesel engine by arranging the secondary balance mechanism 4, and in order to sufficiently lubricate all operating parts in the diesel engine, the diesel engine can further comprise a rotor pump 5. Lubricating oil can be pumped to the oil circuit or parts of the diesel engine through the rotor pump 5 so as to fully lubricate all the running parts of the diesel engine.

Referring to fig. 5, fig. 5 shows a schematic diagram of a process of pumping lubricating oil by the rotor pump 5. The illustrated rotor pump 5, with continuous rotation, sequentially achieves the following actions: negative pressure absorbing lubricating oil as shown in fig. 5 (a); forming a sealed cavity as shown in fig. 5 (b); continuously extruding the lubricating oil as shown in fig. 5 (c); the lubricant is discharged from the pump chamber as shown in fig. 5 (d). The rotor pump 5 circularly executes the above actions to realize the pumping of the lubricating oil.

The present rotor pump 5 is arranged independently on a diesel engine, as shown in fig. 6, which illustrated diesel engine may comprise a cylinder 1, a crankshaft mechanism 2 and a rotor pump 5, wherein the rotor pump 5 is in driving connection with the crankshaft mechanism 2 via a gear transmission, in particular a crankshaft gear 21 of the crankshaft mechanism 2 is in driving connection with the rotor pump 5 via an additionally provided intermediate gear 22. It can be seen that in this arrangement of the rotor pump 5, a plurality of gear pairs are required, the size chain is long, the cumulative tolerance is large, and the NVH (Noise Vibration Harshness noise, vibration and harshness shorthand) performance is poor; as shown in fig. 7, the illustrated diesel engine may include a cylinder 1, a crankshaft mechanism 2 and a rotor pump 5, wherein the rotor pump 5 and the crankshaft mechanism 2 are in transmission connection through a chain transmission mechanism, and the structure is complex because a tensioning structure is required to be arranged in the chain transmission; as shown in fig. 8, the illustrated diesel engine may comprise a cylinder 1, a crankshaft mechanism 2 and a rotor pump 5, wherein the rotor pump 5 is in driving connection with the crankshaft mechanism 2 via a belt drive. The belt transmission mechanism has the defect of poor reliability, so that the running stability of the rotor pump 5 is affected. In all the above three arrangements of the rotor pump 5, an additional arrangement of the transmission mechanism is required, and a large arrangement space is required.

It can be seen that the diesel engine can be provided with a secondary balance mechanism 4 and a rotor pump 5 independently in order to solve the problem of vibration and poor lubrication. However, the space occupied by the independent arrangement of the secondary balance mechanism 4 and the rotor pump 5 is large. In order to achieve the vibration-proof performance, the lubricating performance and the spatial performance, the inventor combines the operation principles of the rotor pump 5 and the secondary balance mechanism 4, and finds that by changing the structure of the rotor pump 5, the rotor pump 5 integrates two functions of pumping lubricating oil and balancing the second-order reciprocating inertial force of the diesel engine. Therefore, the space occupied by the arrangement of the secondary balance mechanism 4 can be reduced. The structure of the rotor pump 5 according to the embodiment of the present invention is specifically described below with reference to the accompanying drawings:

referring to fig. 9 and 10, the diesel engine of the embodiment of the present invention includes a cylinder 1, a crank mechanism 2, an oil pan 3, and a rotor pump 5, wherein the crank mechanism 2 is disposed in the cylinder 1, the rotor pump 5 is disposed in the oil pan 3, a gear of the rotor pump 5 is in driving connection with a crank gear 21 of the crank mechanism 2, and a counterweight is disposed on the rotor pump 5 to counteract a second-order reciprocating inertial force of the diesel engine when the rotor pump 5 rotates following the crank gear 21.

Referring to fig. 10, the rotor pump 5 of the present invention may include a pump housing 51, a gear, a rotor 53, and a balancing weight 54, wherein the pump housing 51 forms a structure supporting the gear 52, the rotor 53, and the balancing weight 54; the rotor 53 rotates following the gear 52; the weight 54 is eccentrically disposed on the rotor 53.

With the rotor pump 5 according to the embodiment of the present invention, since the rotor 53 is eccentrically provided with the balancing weights 54, the rotor pump 5 can counteract the second-order reciprocating inertial force during operation. Thus, the first and second substrates are bonded together,

in the embodiment of the present invention, the pump housing 51 forms a cavity for accommodating the rotor 53, the rotor 53 with the weight 54 mounted thereon is rotatably disposed in the cavity around its own axis, and the gear 52 is disposed outside the cavity and is in driving connection with the rotor 53.

The pump housing 51 includes a liquid outlet and a liquid inlet, both of which are communicated with the cavity, wherein a center line of the liquid outlet and a center line of the liquid inlet are perpendicular to a rotation axis of the rotor 53. Further, the center line of the liquid outlet coincides with the center line of the liquid inlet. In the running process of the rotor pump 5, negative pressure is formed at the liquid inlet to absorb lubricating oil, a sealing cavity is formed, and the lubricating oil is continuously extruded; and discharging the lubricating oil from the liquid outlet.

The pump housing 51 includes a first housing 511 and a second housing 512, where the first housing 511 and the second housing 512 are spliced to form the pump housing 51, and a liquid outlet and a liquid inlet may be formed in the first housing 511 and/or the second housing 512. The first case 511 and the second case 512 are detachably connected or non-detachably connected, and in the detachable connection manner, one of the first case 511 and the second case 512 is provided with a first mounting hole, the other of the two is provided with a second mounting hole aligned with the first mounting hole, and a fastener passes through the first mounting hole and the second mounting hole to connect the first case 511 and the second case 512.

In order to improve the installation convenience, one of the first housing 511 and the second housing 512 is provided with a positioning column, and the other one of the two is provided with a positioning hole matched with the positioning column. When the first housing 511 and the second housing 512 are assembled, preliminary positioning is achieved through cooperation of the positioning posts and the positioning holes, and the fasteners penetrate through the first mounting holes and the second mounting holes, so that mounting of the first housing 511 and the second housing 512 is further achieved.

It should be noted that, the joint surface of the first housing 511 and the second housing 512 is located between the liquid outlet and the liquid inlet, in the illustration, the liquid outlet is located in the first housing 511, and the liquid inlet is located in the second housing 512. With this structure, the sealing requirement of the rotor pump 5 can be satisfied by a lower process.

In some embodiments of the present invention, the splicing surface is parallel to the rotation axis of the rotor 53, and the parallel arrangement is convenient for processing. Further, the splicing surface is perpendicular to the center line of the liquid inlet and the center line of the liquid inlet.

Of course, the liquid outlet and the liquid inlet are both located on the same side of the splicing surface of the first housing 511 and the second housing 512, that is, the liquid outlet and the liquid inlet are both located on the first housing 511, or the liquid outlet and the liquid inlet are both located on the second housing 512.

In some embodiments of the present invention, the housing further includes a mounting groove, and the gear 52 is located in the mounting groove, so that most of the structure of the gear 52 can be covered by the mounting groove, thereby reducing the risk of touching during the installation process of the rotor pump 5, and prolonging the service life of the rotor pump 5.

In the drawing, the gear 52 and the rotor 53 are coaxially arranged on the rotation shaft 55, and in the case where the number of the gears 52 and the number of the rotors 53 are two, the first gear 521 and the first rotor 531 are coaxially arranged on the first rotation shaft 551; the second gear 522 and the second rotor 532 are both coaxially disposed on the second rotational shaft 552. One of the first gear 521 and the second gear 522 is a driving gear 52 to be in driving connection with the crank mechanism 2, and further, may be directly in driving connection with the crank gear 5221 of the crank mechanism 2. The first gear 521 and the second gear 522 are engaged and rotated in opposite directions.

The first gear 521 and the second gear 522 may be spur gears or helical gears. The first gear 521 and the second gear 522 are meshed so that the angular velocities of the first rotor 531 and the second rotor 532 are the same, but opposite directions.

In the above manner of providing two gears 52, the number of gears 52 may be other numbers in some embodiments of the present invention, so long as the same angular velocity of the first rotor 531 and the second rotor 532 can be achieved, but the opposite arrangement number and arrangement manner are all within the protection scope of the present invention.

The first gear 521 and/or the first rotor 531 may be integrally formed with the first shaft 551 or may be formed as a split structure in which the first gear 521 and/or the second rotor 532 may be coupled to the first shaft 551 by means of a key; the second gear 522 and/or the second rotor 532 may be integrally formed with the second shaft 552 or may be separately formed, in which the second gear 522 and/or the second rotor 532 may be coupled to the second shaft 552 by means of a key.

In order to improve the smoothness of the rotor pump 5 during operation, a first bearing is provided between the first rotating shaft 551 and the housing, and a second bearing is provided between the second rotating shaft 552 and the housing.

The above description is of the transmission manner of the gear 52 and the rotor 53, and the following description focuses on the arrangement manner of the rotor 53 and the weight 54.

Referring to fig. 11, the first rotor 531 and the second rotor 532 have the same structure, and the first rotor 531 is described as an example in the embodiment of the present invention.

The first rotor 531 includes a rotor body 5311 and a plurality of rotor arms 5312, the rotor arms 5312 being formed extending radially from the rotor body 5311, the ends of the rotor arms 5312 being in sliding contact with the wall of the housing.

In order to reduce sliding friction between the end of the rotor arm 5312 and the housing wall, the end section of the rotor arm 5312 has a circular arc structure.

Of all rotor arms 5312, part of rotor arms 5312 is provided with a balancing weight 54 and the remainder is not provided with a balancing weight 54, such that the mass centre line of first rotor 531 is offset with respect to the rotation axis, i.e. the mass centre line of first rotor 531 is not coincident with respect to the rotation axis.

In the figure, the number of rotor arms 5312 is three, and only one rotor arm 5312 among the three rotor arms 5312 is provided with a weight 54, and the remaining rotor arms 5312 are not provided with a weight 54, so that the center of mass of the first rotor 531 is offset in a direction approaching the weight 54. Or in still other embodiments of the invention, two rotor arms 5312 are provided with weights 54 and the remaining one rotor arm 5312 is not provided with weights 54 such that the center of mass of the first rotor 531 is offset toward the middle of the two weights 54. Although the illustration discloses a number of rotor arms 5312 of three, the number of rotor arms 5312 may also be two, four, five or six.

Here, it is explained that the density of the weight 54 is greater than that of the first rotor 531. The rotor arm 5312 provided with the weight 54 is provided with an adjustment hole penetrating the rotor arm 5312 in the axial direction of the first rotor 531, and the weight 54 is mounted in the adjustment hole. The shape of the adjustment hole matches the shape of the weight 54, and in the illustration, the weight 54 has a cylindrical structure. The weight 54 may be connected to the adjustment hole by an interference fit or by an adhesive.

To increase the offset of the mass center line of the first rotor 531, in some embodiments of the present invention, the rotor arm 5312 without the balancing weight 54 is provided with a weight reducing hole 5313, so that the mass center line of the first rotor 531 is further offset toward the direction in which the balancing weight 54 is provided.

The weight-reducing hole 5313 may extend through the rotor arm 5312 in the axial direction of the first rotor 531, or may not extend through the rotor arm 5312. The section of the lightening hole is in a regular shape or an irregular shape. Further, the weight-reducing holes may be filled with a filler having a density smaller than that of the rotor 53.

Of the three rotor arms 5312 shown, one rotor arm 5312 is provided with a counterweight 54 and the remaining two rotor arms 5312 are provided with weight-reducing holes 5313.

It should be noted that the counterweight 54 and/or the weight-reducing hole 5313 may be understood as a counterweight.

Referring to fig. 12 in conjunction with fig. 11, fig. 12 illustrates a schematic diagram of the rotor pump 5 counteracting second order reciprocating inertial forces; the rotor pump 5 on which the principle is based comprises a housing, a first rotor 531 and a second rotor 532, the first rotor 531 and the second rotor 532 are each arranged in the cavity of the housing to rotate about their own axes, and the first rotor 531 and the second rotor 532 each comprise three rotor arms 5312, one rotor arm 5312 of the three rotor arms 5312 being provided with a balancing weight 54, the remaining two rotor arms 5312 of the three rotor arms 5312 being provided with a weight-reducing hole 5313.

In the figure, α is the chamfer angle of the connecting line of the first rotor 531 and the second rotor 532 of the rotor pump 5, and satisfies the following conditions:

α＝(360°/z)-90°；

wherein z is the number of cams in the crankshaft mechanism 2;

the center distance between the two rotors 53 is 2a;

R _m a top radius for rotor arm 5312; the rotor arms 5312 with weights 54 of the two rotor arms 5312 are assembled in the same phase, the angular speed of the rotor pump 5 is 2 times the engine speed omega (i.e. 2 omega),in this case.

The stress at the center of gravity of rotor arm 5312 with counterweight 54 is:

F _l1 ＝ω ² ×(D-R _m )×M0；

F _r1 ＝ω ² ×(D-R _m )×M0；

the stresses at the center of gravity of rotor arm 5312 without counterweight 54 are:

F _l2 ＝ω ² ×(D-R _m )×M1；

F _l3 ＝ω ² ×(D-R _m )×M1；

F _r2 ＝ω ² ×(D-R _m )×M1；

F _r3 ＝ω ² ×(D-R _m )×M1；

m0 is the weight of counterweight 54;

m1 is the weight of weight-reducing aperture 5313;

d is the gear pitch diameter of the rotor pump, i.e. d=2×r _D ；；

R _D The radius of the gear reference circle for the rotor pump is equal to the radius of the top circle of the rotor arm 5312;

R _2D for the pitch circle radius of the crankshaft gear, R _2D ＝2R _D ；

These forces undergo horizontal and vertical resolution because the rotation of the two rotor arms 5312 are opposite and in phase.

Component force in horizontal direction:

F _lh1 +F _lh2 +F _lh3 +F _rh1 +F _rh2 +F _rh3 ＝0；

component force in vertical direction:

F _lv1 +F _lv2 +F _lv3 +F _rv1 +F _rv2 +F _rv3 +F _2nd ＝0。

F _2nd is a second-order reciprocating inertial force.

From the flow formula of the rotor pump 5, the flow of the rotor 53 and the top radius R of the rotor 53 _m In relation to the angular velocity (2ω) of the rotor pump 5, in flow determinationAfter that, at R _m It is confirmed that the density ρ of the weight 54 can be adjusted so that M0 satisfies the balanced second-order reciprocating inertial force.

The flow calculation formula:

Q＝ ¹ / ₂ ×λ×π×D2×L×n×η×10 ^-6

wherein:

q, rotor pump 5 flow;

lambda, the area utilization coefficient of the rotor 53 is f (R _m /a)；

L, rotor 53 width;

d, maximum diameter of rotor 53 is 2×R _m ；

n, rotor 53 rotation speed;

η, rotor pump 5 volumetric rate.

Wherein, in the description of the embodiments of the present invention, unless otherwise indicated, "/" means or, for example, a/B may represent a or B; "and/or" herein is merely an association relationship describing an association object, and means that three relationships may exist, for example, a and/or B may mean: a exists alone, A and B exist together, and B exists alone.

The terms "first" and "second" are used above for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature.

For convenience of description, only a portion related to the present invention is shown in the drawings. Embodiments of the invention and features of the embodiments may be combined with each other without conflict.

The above description is only illustrative of the preferred embodiments of the present invention and the technical principles applied, and is not intended to limit the present invention. Various modifications and variations of the present invention will be apparent to those skilled in the art. The scope of the invention is not limited to the specific combination of the above technical features, but also covers other technical features formed by any combination of the above technical features or their equivalents without departing from the inventive concept. Such as the above-mentioned features and the technical features disclosed in the present invention (but not limited to) having similar functions are replaced with each other.

Claims (12)

1. A rotor pump comprising a pump housing, a gear, a rotor, and a counterweight, wherein the pump housing forms a structure that supports the gear, the rotor, and the counterweight; the rotor rotates along with the gear; the balancing weight is eccentrically arranged on the rotor.

2. A rotor pump as claimed in claim 1, wherein the pump housing defines a cavity for receiving the rotor, the rotor being rotatably disposed within the cavity about its own axis, the gear being located outside the cavity and in driving connection with the rotor.

3. The rotor pump as claimed in claim 2, wherein a center line of the liquid outlet and a center line of the liquid inlet of the pump housing are perpendicular to the rotation axis of the rotor.

4. A rotor pump as claimed in claim 3, wherein the pump housing comprises a first housing and a second housing, the first housing and the second housing being spliced to form the pump housing, the liquid outlet and the liquid inlet being formable in the first housing and/or the second housing.

5. The rotor pump as claimed in claim 4, wherein the first housing and the second housing are detachably connected or non-detachably connected.

6. A rotor pump according to claim 3, wherein the number of gears and the number of rotors are two, specifically, a first gear and a first rotor are coaxially arranged on a first rotating shaft, and a second gear and a second rotor are coaxially arranged on a second rotating shaft.

7. The rotor pump as claimed in claim 6, wherein the angular velocities of the first rotor and the second rotor are the same and opposite.

8. The rotor pump as claimed in claim 7, wherein the first rotor and the second rotor are identical in structure.

9. A rotor pump according to any one of claims 1 to 8, wherein the rotor comprises a rotor body and a plurality of rotor arms formed extending radially from the rotor body, the ends of the rotor arms being in sliding contact with the wall of the housing; the balancing weights comprise balancing weights, part of the rotor arms are provided with the balancing weights, the balance weights are not arranged on the rest of the rotor arms, so that the mass center line of the rotor is offset relative to the rotation axis, and the density of the balancing weights is larger than that of the rotor.

10. The rotor pump according to claim 9, wherein the balancing weight further comprises a weight-reducing hole provided on the rotor arm where the balancing weight is not provided among all the rotor arms.

11. A rotor pump according to claim 9, wherein the rotor arm provided with the balancing weight is provided with an adjustment hole in which the balancing weight is mounted.

12. A diesel engine, comprising a cylinder, a crank mechanism, an oil pan and a rotor pump, wherein the crank mechanism is arranged in the cylinder, the rotor pump is arranged in the oil pan, the rotor pump is as claimed in any one of claims 1 to 11, and a gear of the rotor pump is in transmission connection with a crank gear of the crank mechanism.