CN218913150U

CN218913150U - Ignition oil pump of boiler fuel system

Info

Publication number: CN218913150U
Application number: CN202223292910.0U
Authority: CN
Inventors: 刘勇强; 舒锦; 汪志威; 鲍林; 仇文辉
Original assignee: Huangshan Huang Pump Twin Screw Technology Co ltd
Current assignee: Huangshan Huang Pump Twin Screw Technology Co ltd
Priority date: 2022-12-08
Filing date: 2022-12-08
Publication date: 2023-04-25
Anticipated expiration: 2032-12-08

Abstract

The utility model discloses an ignition oil pump of a boiler fuel system, which comprises an inlet cavity, an outlet cavity, a suction cavity, a driving screw rod, a driven screw rod and a plurality of cavities. The two ends of the outlet cavity are sequentially spliced with at least one cavity, the inlet cavity is connected to the end part of the leftmost cavity of the outlet cavity, and the suction cavity is connected to the end part of the rightmost cavity of the outlet cavity; an inlet flange is arranged on the side wall of the inlet cavity, and a conveyed medium is sucked into the pump body through the inlet flange; an outlet flange is arranged on the side wall of the outlet cavity, and the conveyed medium is discharged out of the pump body through the outlet flange; the side walls of the suction cavity and the inlet cavity are also connected with a drainage tube which communicates the suction cavity and the inlet cavity. The utility model can output stable flow with high efficiency under higher ignition oil supply pressure, has long service life and ensures long-term reliable and stable operation of the boiler unit.

Description

Ignition oil pump of boiler fuel system

Technical Field

The utility model relates to the field of boiler fuel system equipment, in particular to an ignition oil pump of a boiler fuel system.

Background

The boiler fuel system is an auxiliary combustion system of a power plant boiler, and has the main function of providing auxiliary fuel when the unit is started and the load changes, so that the safe and reliable operation of the boiler unit is ensured.

In order to make the ignition of the unit smooth, the fuel oil burns fully, the fuel oil of the boiler must enter the boiler to burn in a high-quality atomization form, so that the fuel oil entering the fuel oil nozzle of the boiler is required to have higher pressure, the ignition fuel supply pressure generally reaches at least 2.5MPa, and along with the continuous improvement of the requirements of the boiler system, the condition that the ignition fuel supply pressure reaches 4.0MPa is more and more, so that the higher requirements are put forward for the ignition fuel pump of the boiler.

At present, a three-screw pump is used as an ignition oil pump of a boiler, but the service life of the three-screw pump is generally within 6 months under the ignition oil supply pressure of 2.5MPa, and the ignition oil supply pressure of 4.0MPa cannot be met due to the fact that the viscosity of fuel oil is low, the oil supply pressure is high, and the abrasion of the pump is very fast. In addition, the fuel flow requirement of the boiler fuel system is smaller to be less than or equal to 20m ³ And/h is high, so that the multistage centrifugal pump is not suitable for the high-pressure small-flow working condition.

Therefore, how to provide a more stable ignition oil pump for a boiler fuel system is a technical problem to be solved in the art.

Disclosure of Invention

The utility model aims to provide an ignition oil pump of a boiler fuel system, which can efficiently output stable flow under higher ignition oil supply pressure, has long service life and ensures long-term reliable and stable operation of a boiler unit.

According to one aspect of the utility model, there is provided a boiler fuel system ignition oil pump comprising an inlet chamber, an outlet chamber, a suction chamber, a driving screw, a driven screw, and a plurality of chambers;

the two ends of the outlet cavity are sequentially spliced with at least one cavity, the inlet cavity is connected to the end part of the leftmost cavity of the outlet cavity, and the suction cavity is connected to the end part of the rightmost cavity of the outlet cavity; an inlet flange is arranged on the side wall of the inlet cavity, and a conveyed medium is sucked into the pump body through the inlet flange; an outlet flange is arranged on the side wall of the outlet cavity, and the conveyed medium is discharged out of the pump body through the outlet flange; the side walls of the suction cavity and the inlet cavity are also connected with a drainage tube which communicates the suction cavity and the inlet cavity;

the end of the inlet cavity and the end of the suction cavity are also provided with bearing seats, the driving screw and the driven screw are meshed with each other, two ends of the driving screw and the driven screw are respectively fixed on the bearing seats through bearings, the driving screw and the driven screw are centered on the outlet cavity, two sides of the driving screw are respectively provided with threads with opposite rotation directions, one end of the driving screw extends to the outer side of the suction cavity and is connected with driving equipment, so that a conveyed medium can be conveyed from the inlet cavity and the suction cavity towards the outlet cavity to realize bidirectional conveying.

Optionally, according to the ignition oil pump of the boiler fuel system of the present utility model, two side surfaces of the cavity are all in a mutually parallel ladder shape, two side surfaces of the outlet cavity are respectively matched with side surfaces of the cavities at two ends, and opposite side surfaces of the suction cavity and the inlet cavity are respectively matched with the side surfaces of the cavities.

Optionally, according to the ignition oil pump of the boiler fuel system provided by the utility model, a plurality of groups of corresponding compression blocks are arranged on the outer side walls of the suction cavity and the inlet cavity, and the opposite compression blocks are fastened and connected through stud bolts, so that the inlet cavity, the outlet cavity, the suction cavity and the plurality of cavities form an integral structure.

Optionally, according to the boiler fuel system ignition oil pump of the present utility model, the sidewall bottoms of the inlet chamber and the outlet chamber are both provided with brackets to serve as mounting feet for the pump.

Optionally, according to the boiler fuel system ignition oil pump of the present utility model, the drainage tube is disposed at the bottom of the side wall of the inlet chamber and the outlet chamber.

Optionally, according to the ignition oil pump of the boiler fuel system, one end of the driving screw rod and one end of the driven screw rod, which are close to the inlet cavity, extend to the outer side of the inlet cavity and are meshed and driven through a gear pair.

Optionally, according to the ignition oil pump of the boiler fuel system of the present utility model, a gap delta is left between the driving screw and the driven screw and the inner side wall of the pump body respectively.

Optionally, the value of the clearance delta is within 0.1-0.2 mm according to the ignition oil pump of the boiler fuel system.

Optionally, according to the ignition oil pump of the boiler fuel system of the present utility model, a plurality of throttling grooves are processed on the inner side wall of each cavity and the inner side wall of the outlet cavity, an included angle α exists between the throttling grooves and tooth top surfaces of the driving screw and the driven screw, and the included angle α faces the suction cavity and the inlet cavity respectively.

Optionally, according to the ignition oil pump of the boiler fuel system of the present utility model, the included angle α is in the range of 30 ° to 45 °, the width b of the throttling groove is 3 to 5mm, the depth h is 3 to 5mm, and the space s between adjacent throttling grooves is 0.5 times the width b of the throttling groove.

The utility model has the following advantages:

(1) The double-suction screw structure of the ignition oil pump of the boiler fuel system enables axial force to be balanced, and the pump has the capability of adapting to high-pressure working conditions. The screw is driven by the gear, a gap exists between the screw and the pump body, no abrasion exists, and the service life is long.

(2) The lead size and the thread length of the threads on the screw rod are adjusted along with the change of the outlet pressure of the ignition oil pump so that the pump can reach different pressure boosting capacities, and therefore the pump with the same specification has screws with various specifications. According to the utility model, the screws with different specifications can be met by adaptively adjusting the length and the number of the chambers (without changing and reforming the whole pump body), so that the ignition oil pump meets the working condition requirements of different ignition oil supply pressures.

(3) Be provided with the throttling groove on the pump body hole face mutually supporting with the screw rod excircle, integral single part structure pump body, the pump body will be very long, and whole hole is very dark for throttling groove processing degree of difficulty is very big, and throttling groove is difficult to implement. The existing structure only needs to be processed on the cavity with the shorter length and the outlet cavity respectively, so that the processing difficulty of the throttling groove is greatly reduced, and the feasibility of the throttling groove is high.

(4) If the pump body has local unexpected abrasion failure, only the corresponding abrasion parts, such as the cavity or the outlet cavity, need to be replaced, and the use and maintenance cost is low.

(5) The outer circle of the screw rod and the inner hole of the matched pump body keep a mounting clearance delta, so that conveyed materials flow back from the high pressure side to the low pressure side along the clearance delta.

Other features of the present utility model and its advantages will become apparent from the following detailed description of exemplary embodiments of the utility model, which proceeds with reference to the accompanying drawings.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description, serve to explain the principles of the utility model.

FIG. 1 is a cross-sectional view of an ignition oil pump of a disclosed boiler fuel system;

FIG. 2 is a front view of an ignition oil pump of the disclosed boiler fuel system;

FIG. 3 is a side view of an ignition oil pump of the disclosed boiler fuel system;

FIG. 4 is a schematic view of the structure of the throttle slot and gap delta disclosed in the present utility model;

fig. 5 is an enlarged view of a portion of the throttle groove and gap delta of fig. 4 in accordance with the present utility model.

Reference numerals illustrate: 01-driving screw; 02-a driven screw; 03-an inlet flange; 04-outlet flange; 05-bearing seats; 06-an inhalation chamber; 07-a chamber; 08-exit chamber; 09-an inlet chamber; 10-a gear pair; 11-a bearing; 12-compacting blocks; 13-stud bolts; 14-a bracket; 15-drainage tube; 16-throttling groove.

Detailed Description

Various exemplary embodiments of the present utility model will now be described in detail with reference to the accompanying drawings. It should be noted that: the relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise.

The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses.

Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.

In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of exemplary embodiments may have different values.

It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

According to fig. 1 to 5, the utility model provides an ignition oil pump of a boiler fuel system, which comprises an inlet cavity 09, an outlet cavity 08, a suction cavity 06, a driving screw 01, a driven screw 02 and a plurality of cavities 07.

At least one cavity 07 is spliced at two ends of the outlet cavity 08 in sequence, the inlet cavity 09 is connected with the end part of the cavity 07 at the leftmost side of the outlet cavity 08, and the suction cavity 06 is connected with the end part of the cavity 07 at the rightmost side of the outlet cavity 08; an inlet flange 03 is arranged on the side wall of the inlet cavity 09, and a conveyed medium is sucked into the pump body through the inlet flange 03; an outlet flange 04 is arranged on the side wall of the outlet cavity 08, and the conveyed medium is discharged out of the pump body through the outlet flange 04; the side walls of the suction cavity 06 and the inlet cavity 09 are also connected with a drainage tube 15 which communicates the suction cavity 06 and the inlet cavity 09.

The end of inlet cavity 09 and suction cavity 06 still is equipped with bearing frame 05, and initiative screw rod 01 and driven screw rod 02 intermesh, and its both ends are fixed respectively on bearing frame 05 through bearing 11, and initiative screw rod 01 and driven screw rod 02 regard outlet cavity 08 as the center, and its both sides are equipped with the screw thread that revolves the opposite direction respectively, and the one end of initiative screw rod 01 extends to the outside of suction cavity 06 and is connected with actuating device to make and be carried the medium and can realize two-way transport from inlet cavity 09 and suction cavity 06 towards outlet cavity 08.

In this embodiment, the lead and the thread length of the threads on the driving screw 01 and the driven screw 02 are adjusted according to the change of the outlet pressure of the ignition oil pump, so that the pump achieves different pressure boosting capacities, and therefore, the pump with the same specification has screws with various specifications. The utility model can meet the screw rods with different specifications by only adaptively adjusting the length and the number of the chambers 07 (without changing and reforming the whole pump body), thereby enabling the ignition oil pump to meet the working condition demands of different ignition oil supply pressures. If the pump body has a local unexpected abrasion fault, only the corresponding abrasion parts, such as the cavity 07 or the outlet cavity 08, need to be replaced, and the use and maintenance cost is low. The inlet flange direction of the illustrated pump is right-side (seen from the shaft head to the pump), and only the mounting positions of the suction cavity 06 and the inlet cavity 09 are changed, so that the inlet flange direction of the pump can be changed into left-side, thereby meeting the demands of unused pipeline arrangement.

Still further, both side surfaces of the chamber 07 are in a stepped shape parallel to each other, both side surfaces of the outlet chamber 08 are respectively engaged with side surfaces of the chambers 07 at both ends, and opposite side surfaces of the suction chamber 06 and the inlet chamber 09 are respectively engaged with side surfaces of the engaged chamber 07. A positive fit connection between the chambers 07 or between the outlet chamber 08, the inlet chamber 09 and the suction chamber 06 is ensured, and a corresponding sealing gasket can be provided between the connection surfaces of each layer.

Still further, be equipped with multiunit corresponding compact heap 12 on the lateral wall of suction chamber 06 and import chamber 09, through stud 13 fastening connection between the relative compact heap 12, combine sealed the pad for through stud 13's regulation, suction chamber 09, export chamber 08, suction chamber 06 and a plurality of cavity 07 form overall structure.

Still further, the sidewall bottoms of both the inlet chamber 09 and the outlet chamber 08 are provided with brackets 14 to serve as mounting feet for the pump.

Still further, a draft tube 15 is provided at the bottom of the side walls of the inlet chamber 09 and the outlet chamber 08. In the embodiment, the conveyed material enters from the inlet flange 03 and is positioned at the bottom of the inlet cavity 09 under the action of dead weight, the drainage tube 15 is connected to the bottoms of the inlet cavity 09 and the suction cavity 06, and the conveyed material is conveyed to one side of the suction cavity 06 through the drainage tube 15 by combining the rotary conveying of the driving screw 01 and the driven screw 02, so that the bidirectional conveying of the pump body is realized.

Still further, one end of the driving screw 01 and the driven screw 02 near the inlet chamber 09 extends to the outside of the inlet chamber 09, and is engaged with and driven by the gear pair 10. The gear pair 10 is located outside the inlet chamber 09 and is closed by a corresponding cover, which serves to protect the driving screw 01 and the driven screw 02 and to prevent the substance to be conveyed from affecting the meshing transmission of the two.

Further, a gap delta is reserved between the driving screw 01 and the driven screw 02 and the inner side wall of the pump body, so that a flowing gap exists between the screw and the pump body, and the pump has no abrasion and long service life. The value of the gap delta is within 0.1-0.2 mm according to the different pressure and pump specifications.

Still further, a plurality of throttling grooves 16 are formed on the inner side wall of each chamber 07 and the inner side wall of the outlet chamber 08, and an included angle alpha exists between the throttling grooves 16 and tooth tops of the driving screw 01 and the driven screw 02, and the included angle alpha faces the suction chamber 06 and the inlet chamber 09 respectively. The outer circle of the screw rod and the inner hole of the pump body which are matched with the screw rod keep a mounting clearance delta, so that conveyed materials flow back from the high pressure side to the low pressure side along the clearance delta (a backflow direction 1 shown in a fifth drawing), and the higher the pressure is, the larger the backflow amount is, so that the efficiency of the pump is greatly influenced. The utility model is provided with a plurality of throttling grooves 16 on the inner hole surfaces of the chamber 07 and the outlet chamber 08 which are matched with the outer circle of the screw. On the one hand: when the backflow liquid enters the throttling groove 16 from the gap delta, the flow area of the backflow channel is suddenly increased, a fluid vortex is formed in the throttling groove 16, potential energy of the backflow liquid is reduced, and the backflow channel is subjected to combined action of a plurality of continuous throttling grooves 16, so that a labyrinth sealing effect is formed in the backflow channel, effective throttling is formed on the backflow quantity of the liquid, and the backflow quantity is reduced. On the other hand: when the backflow liquid enters the throttling groove 16, the liquid flows along the throttling groove 16 to form a backflow direction 2 opposite to the backflow direction 1, so that the backflow direction 1 generates larger resistance drop, the pressure of the throttling groove 16 is effectively reduced, and therefore throttling and quantity reducing effects are generated on the backflow quantity of the liquid. The arrangement of the throttling groove 16 effectively improves the efficiency of the ignition oil pump of the boiler fuel system, and ensures that the pump can be normally used under high ignition oil supply pressure.

Still further, the included angle α is in the range of 30 ° to 45 °, the width b of the throttling groove 16 is 3 to 5mm, the depth h is 3 to 5mm, and the space s between adjacent throttling grooves 16 is 0.5 times the width b of the throttling groove 16, which has good throttling effect and high practicality.

In addition, compared with the integral pump body structure in the prior art, the integral pump body with the single part structure is long, the whole inner hole is deep, so that the processing difficulty of the throttling groove 16 is high, and the throttling groove 16 is difficult to implement. The utility model only needs to be respectively processed on the chamber 07 with a shorter length and the outlet chamber 08, so that the processing difficulty of the throttling groove 16 is greatly reduced, and the feasibility of the throttling groove 16 is high.

While certain specific embodiments of the utility model have been described in detail by way of example, it will be appreciated by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the utility model. It will be appreciated by those skilled in the art that modifications may be made to the above embodiments without departing from the scope and spirit of the utility model. The scope of the utility model is defined by the appended claims.

Claims

1. The ignition oil pump of the boiler fuel system is characterized by comprising an inlet cavity, an outlet cavity, a suction cavity, a driving screw rod, a driven screw rod and a plurality of cavities;

2. The ignition oil pump of a boiler fuel system according to claim 1, wherein both side surfaces of the chamber are in a mutually parallel stepped shape, both side surfaces of the outlet chamber are respectively matched with the side surfaces of the chambers at both ends, and the opposite side surfaces of the suction chamber and the inlet chamber are respectively matched with the side surfaces of the chambers which are matched.

3. The boiler fuel system ignition oil pump according to claim 2, wherein a plurality of groups of corresponding compression blocks are arranged on the outer side walls of the suction cavity and the inlet cavity, and the opposite compression blocks are fastened and connected through stud bolts, so that the inlet cavity, the outlet cavity, the suction cavity and the plurality of cavities form an integral structure.

4. A boiler fuel system ignition oil pump according to claim 3, characterized in that the sidewall bottoms of the inlet and outlet chambers are provided with brackets for use as mounting feet for the pump.

5. The boiler fuel system ignition oil pump of claim 4, wherein said draft tube is disposed at the bottom of the sidewall of said inlet and outlet chambers.

6. The boiler fuel system ignition oil pump of claim 1, characterized in that one end of said driving screw and said driven screw near said inlet chamber extend to the outside of said inlet chamber and are driven by gear pair engagement.

7. The boiler fuel system ignition oil pump according to any one of claims 1 to 6, wherein a gap δ is left between the driving screw and the driven screw, respectively, and an inner sidewall of the pump body.

8. The boiler fuel system ignition oil pump of claim 7, wherein the value of the gap δ is within 0.1-0.2 mm.

9. The boiler fuel system ignition oil pump of claim 7, characterized in that a plurality of throttling grooves are processed on the inner side walls of each chamber and the outlet chamber, and an included angle alpha exists between the throttling grooves and tooth top surfaces of the driving screw and the driven screw, and the included angle alpha faces the suction chamber and the inlet chamber respectively.

10. The boiler fuel system ignition oil pump according to claim 9, characterized in that the angle of the included angle α is in the range of 30 ° to 45 °, the width b of the throttling groove is 3 to 5mm, the depth h is 3 to 5mm, and the spacing s between adjacent throttling grooves is 0.5 times the width b of the throttling groove.