CN201100380Y - Line reciprocating joint machine for opposite crank sliding block - Google Patents
Line reciprocating joint machine for opposite crank sliding block Download PDFInfo
- Publication number
- CN201100380Y CN201100380Y CNU200720043957XU CN200720043957U CN201100380Y CN 201100380 Y CN201100380 Y CN 201100380Y CN U200720043957X U CNU200720043957X U CN U200720043957XU CN 200720043957 U CN200720043957 U CN 200720043957U CN 201100380 Y CN201100380 Y CN 201100380Y
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- Prior art keywords
- crosshead
- connecting rod
- pump
- opposed type
- line reciprocating
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- 230000007246 mechanism Effects 0.000 claims abstract description 19
- 230000033001 locomotion Effects 0.000 claims description 16
- 239000012530 fluid Substances 0.000 claims description 15
- 230000009347 mechanical transmission Effects 0.000 abstract description 2
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 230000000737 periodic effect Effects 0.000 description 3
- 241001347978 Major minor Species 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000003190 augmentative effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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Abstract
The utility model relates to an opposite crank block straight reciprocating link mechanism, belonging to the technical field of a mechanical transmission device, comprising a crankshaft which is supported on a body; and a connecting rod, wherein one end is hinged with the crankshaft, and the other end is hinged with a reciprocating slide block. The slide block is composed of the fixed connection between a main crosshead and an auxiliary crosshead which are separately arranged on two sides of the crankshaft. The main crosshead and the auxiliary crosshead compose a shifting pair separately with synclastic guide rails which are disposed on two sides of the body. After the opposite crank block straight reciprocating link mechanism is applied, the piston force which is exerted on the power-end crank mechanism is in a structural equilibrium state, thereby being able to effectively avoid 'burning bearings'; the guiding length of the shifting pair is notably increased, thereby the moving precision of the hydraulic-end plunger is improved; the unit pressure (intensity of pressure, viz. p) which is acted on a connecting rod large end bush in the crank mechanism can be effectively decreased, or the transport flow capacity of a pump can be increased under the situation of not increasing the unit pressure (intensity of pressure, viz. p) which is acted on the connecting rod large end bush.
Description
Technical field
The utility model relates to a kind of crank block double-action mechanism, and especially a kind of straight line reciprocating interlocking mechanism of opposed type crank block belongs to the technical field of mechanical transmission.
Background technique
Existing oil field with the typical structure of boosting water injection pump (3ZY8/40 type) as depicted in figs. 1 and 2, its power end has constituted the multi-joint connecting rod group of typical three crank throws by fuselage 1, bent axle 2, connecting rod 3 and crosshead (slide block) 4.During work: motor via reducer drives bent axle, and under the constraint of selfaligning roller bearing on the axle, bent axle is around self axis rotation; Under the drive of crank section, connecting rod tip is made circular movement around crankshaft center line; Wrist-pin end of connecting rod transmits motion on the crosshead hinged with it, and under the constraint of pump housing slideway, this crosshead is done straight reciprocating motion along slideway; Under the driving of crosshead, it is reciprocating together that pump plunger is followed; The to-and-fro motion of plunger makes the plunger cavity of pump hydraulic end produce periodic volume-variation, and be transferred medium and under the control of fluid end valve assembly, finish the process that sucks discharge, and the periodic duty that goes round and begins again.
In the horizontal plunger pump of three cylinder single-actings of this class formation, three cylinders are the side of horizontal arrangement at bent axle, be subjected to this structural limitations, have following drawback: 1. the piston force that bears on the connecting rod bottom bearing is one-sided all the time, and in load by zero during to the maximum value alternate, it acts on the bearing area fixed-site of connecting rod bearing shell inwall constant (being that the connecting rod bearing shell inwall bears pressure and frictional force all the time on a position), cause connecting rod bearing shell inwall long-term existence to be subjected to force unbalance, cause the aggravation of inwall uneven wear, destroy the formation condition of pressure-bearing oil film between connecting rod bearing shell inwall and the crank pin cylindrical, be directed at generation " tile kilning " fruit afterwards.2. the Operational Limits of pump is restricted: during a. pump work, the size of flow parameter is relevant with the running length of pump speed, plunger (piston) diameter and plunger (piston).For augmented flow, it also is limited adopting the raising pump speed, because the limit reciprocal time of pump is subjected to the restriction that valve opens and closes the hysteresis quality of speed; Adopt to increase plunger (piston) diameter or increase running length and but will increase the pump structure size.B. when the pressure one of pump regularly, it is relevant with the size of the active area of plunger (piston) to act on crankshaft bearing liner (connecting rod bearing shell) piston force.So the pump that three cylinder single-actings are arranged under certain delivery pressure, its crankshaft bearing liner (connecting rod bearing shell) will bear bigger piston force.This also is disadvantageous for pump.
The model utility content
The purpose of this utility model is: at the shortcoming of above prior art existence, the straight line reciprocating interlocking mechanism of opposed type crank block of stress equalization on a kind of connecting rod bottom bearing is proposed, thereby the uneven wear that the series products that is used to avoid boosting water injection pump exists is stopped " tile kilning " phenomenon.
In order to reach above purpose, straight line reciprocating interlocking mechanism of opposed type crank block of the present utility model comprises the bent axle that is supported on the fuselage, one end and bent axle are hinged, the other end and the hinged connecting rod of to-and-fro motion slide block (being commonly called as crosshead), its improvements are: described slide block is a kit form, being connected by main crosshead that lays respectively at the bent axle both sides and secondary crosshead constitutes, and described main crosshead and secondary crosshead constitute sliding pair with the guide rail in the same way at fuselage two places respectively.
Above-mentioned straight line reciprocating interlocking mechanism of opposed type crank block of the present utility model is compared with the single-sided arrangement structure of conventional reciprocating pump after being applied in the product of water injection pump and so on, obviously has following advantage:
1, can make the piston force that puts on the power end crank mechanism be in structural state of equilibrium.The bearing shell stress area of connecting rod tip is symmetry status and distributes, and connecting rod bearing shell inwall movement pair surface uneven wear situation is able to basic improvement, has protected the formation condition of the pressure-bearing oil film between the kinematic pair, can avoid " tile kilning " effectively.
2, the guiding length phenomenal growth of sliding pair helps to make the to-and-fro motion of crosshead smooth more and steady, thereby the kinematic accuracy of fluid end plunger is improved.
3, the pump of determining for Operational Limits can make the piston force that acts on the crank mechanism be reduced effectively or increase the feed flow of pump under the situation that does not increase piston force.
Description of drawings
Below in conjunction with accompanying drawing the utility model is further described.
Fig. 1 is an existing oil field boosting water injection pump structural representation.
Fig. 2 is the plan view of Fig. 1.
Fig. 3 is the structure for amplifying schematic representation of opposed type slide block linked component in the straight line reciprocating interlocking mechanism of opposed type crank block.
Fig. 4 is an embodiment's of the utility model a structural representation.
Fig. 5 is the plan view of Fig. 4.
Embodiment
Embodiment one
The straight line reciprocating interlocking mechanism of opposed type crank block practical application of present embodiment in the oil field with the situation of boosting water injection pump as shown in Figure 4 and Figure 5, integral body is that six cylinder flat opposed formulas are arranged the single-acting reciprocating pump, as the pump of multi-joint forms of motion, its main composition partly comprises two ends opposed type fluid end 7 and power end two-part.The main member of forming power end has the fuselage 1 of three-throw crankshaft 2, connecting rod 3, opposed type slide block (crosshead) linked component 4 and connection and supporting power end and fluid end.Bent axle 2 is supported on the fuselage 1 by near the selfaligning roller bearing the two ends, and the control of the axial assemblage gap of whole crankshaft group is realized by the adjustment of the axial dimension of end cap, tail-hood and bearing housing.The motive force of pump is motor, links by speed reducer (belt pulley) and pump.The big end of each connecting rod 3 is hinged with the corresponding position of bent axle 2 respectively, and small end is hinged by crosshead bearing pin 5 with reciprocating linked component respectively.
The concrete structure of opposed type slide block (crosshead) linear reciprocation linked component 4 constitutes repeatedly by the main crosshead 4-5 that lays respectively at the bent axle both sides and secondary crosshead 4-1 are fixing as shown in Figure 3.Concrete linkage structure is between main crosshead 4-5 and secondary crosshead 4-1 four jiaos four hollow connecting rod 4-3 that separate to be housed respectively, the two ends of each connecting rod 4-3 are shaped on counterbore respectively, main crosshead 4-5 and secondary crosshead 4-1 relative position are shaped on positioning hole corresponding, the external diameter of location cylinder 4-4 cooperates with described counterbore and positioning hole, counterbore and the positioning hole on the other side of connecting rod 4-3 inserted at its two ends respectively, realize relative positioning axial and radially, four bolt 4-2 pass secondary crosshead 4-1 respectively, the center hole of location cylinder 4-4 and connecting rod 4-3, be screwed on the main crosshead 4-5, making main crosshead fixedlyed connected with secondary crosshead becomes the integral body of rigidity.Main crosshead 4-5 and secondary crosshead 4-1 respectively with fuselage 1 on major and minor crosshead slideway form sliding pair.
The crosshead of these opposed type slide block (crosshead) linked component 4 both sides links to each other with the plunger of the fluid end 7 at pump two ends respectively, makes the pump structure form become fluid cylinder opposed type horizontal arrangement by the one-sided horizontal arrangement of original fluid cylinder.
During pump work, motor via reducer (or belt pulley) drives bent axle, and under the constraint of selfaligning roller bearing on the axle, bent axle is around self axis rotation; Simultaneously the crankshaft crank part is being that radius is made circular movement around crankshaft center line with its center of circle to the distance of crankshaft center line; Under the driving of crank section, the big end movement therewith of connecting rod is also passed through connecting rod shank, wrist-pin end of connecting rod, transmit motion on opposed type slide block (crosshead) linked component hinged with it, under the constraint of pump housing slideway, opposed type slide block (crosshead) linked component is done straight reciprocating motion along fuselage major-minor slideway; Under the driving of the major-minor crosshead at two ends, it is reciprocating together that the plunger in the fluid cylinder of two ends is followed crosshead; Along with the to-and-fro motion of plunger, the plunger cavity of pump hydraulic end produces periodic volume-variation, is transferred medium along with plunger cavity periodicity volume-variation, finishes sucking the process of discharging under the control of fluid end valve assembly, and the work that goes round and begins again.
This reciprocal technical data required for the pump relation is as follows:
Flow Q=nZAS60 (m
3/ h)
Pressure p=F/A (MPa; N/m
2Kgf/cm
2)
In the formula: n-pump speed; A-piston action area (π D
2/ 4m
2); P-head pressure; F-piston force (Newton; Kgf); S-stroke (m); Z-fluid cylinder number.
From the formula of above-mentioned reciprocating pump performance parameter, be not difficult to find out, after the head pressure p of pump determines with the device condition, when the close limit of pump speed n, when stroke S is definite value, if will increase the flow of pump, increase the piston action area A as adopting, then piston force F just increases thereupon.The unit pressure (being pressure P) that acts on connecting rod bottom bearing will become big.Usually, the PV in the life-span of connecting rod bearing shell and its motion (product of the movement velocity when pressure that surface of friction pair bore and friction) value is inversely proportional to.The method that increases flow with increase piston action area will cause connecting rod bearing shell friction pair PV value to increase, and the life-span lowers.Obviously, count the increase that Z just can avoid increasing realization flow under the situation of the unit pressure (being pressure p) that acts on connecting rod bottom bearing by adopting the opposed type structure to increase fluid cylinder.
Otherwise, as the flow Q of pump; When head pressure p and pump speed n and stroke S are definite value, if adopt opposed type fluid cylinder structure (promptly adopting the crosshead kinematic pair of opposed type structure), making the pump fluid cylinder count Z doubles, the active area that this measure can make each piston is reducing under the constant situation of half and the resultant action area of piston, finish above-mentioned performance parameter, and this moment, the unit pressure (being pressure p) that acts on the crank mechanism connecting rod bottom bearing just can reduce half.This improvement for the working condition of connecting rod bottom bearing is self-evident.
In addition to the implementation, the utility model can also have other mode of executions.All employings are equal to the technological scheme of replacement or equivalent transformation formation, all drop on the protection domain of the utility model requirement.
Claims (4)
1, a kind of straight line reciprocating interlocking mechanism of opposed type crank block, comprise the bent axle that is supported on the fuselage, one end and bent axle are hinged, the other end and the hinged connecting rod of to-and-fro motion slide block, it is characterized in that: described slide block is a kit form, being connected by main crosshead that lays respectively at the bent axle both sides and secondary crosshead constitutes, and described main crosshead and secondary crosshead constitute sliding pair with the guide rail in the same way at fuselage two places respectively.
2, according to the described straight line reciprocating interlocking mechanism of opposed type crank block of claim 1, it is characterized in that: four hollow connecting rods are housed respectively between four jiaos of described main crosshead and secondary crosshead, and pass four bolt respectively and connect into rigid unitary.
3, according to the described straight line reciprocating interlocking mechanism of opposed type crank block of claim 2, it is characterized in that: the two ends of described each connecting rod are shaped on counterbore respectively, described main crosshead and secondary crosshead relative position are shaped on positioning hole corresponding, insert the location cylinder location that external diameter matches with it in described counterbore and the positioning hole.
4, according to the described straight line reciprocating interlocking mechanism of opposed type crank block of claim 3, it is characterized in that: fluid end is equipped with at described fuselage two ends respectively, and described main crosshead and secondary crosshead link to each other with plunger with two fluid ends respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720043957XU CN201100380Y (en) | 2007-09-29 | 2007-09-29 | Line reciprocating joint machine for opposite crank sliding block |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720043957XU CN201100380Y (en) | 2007-09-29 | 2007-09-29 | Line reciprocating joint machine for opposite crank sliding block |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201100380Y true CN201100380Y (en) | 2008-08-13 |
Family
ID=39936916
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU200720043957XU Expired - Fee Related CN201100380Y (en) | 2007-09-29 | 2007-09-29 | Line reciprocating joint machine for opposite crank sliding block |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201100380Y (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101813170A (en) * | 2009-10-16 | 2010-08-25 | 北京中清能发动机技术有限公司 | Mechanism for mutual conversion between reciprocating motion and rotating motion, part and device thereof |
| CN106809452A (en) * | 2017-04-16 | 2017-06-09 | 浙江江南制药机械有限公司 | A kind of roller plate blister packaging machine is horizontally-opposed to be punched and beats lot number integrated device |
| CN107598036A (en) * | 2017-11-01 | 2018-01-19 | 王流洋 | A kind of double cut-out station bar croppers |
| CN109162894A (en) * | 2018-08-07 | 2019-01-08 | 中国石油大学(北京) | Sulfur resistive compressor |
| CN109826777A (en) * | 2019-01-29 | 2019-05-31 | 四川金星清洁能源装备股份有限公司 | Two-way crosshead transmission mechanism for Reciprocting piston compressor |
| CN110397382A (en) * | 2018-07-27 | 2019-11-01 | 襄阳市思想机电科技有限公司 | A kind of multi-connecting-rod mechanism |
| CN110397381A (en) * | 2018-07-27 | 2019-11-01 | 襄阳市思想机电科技有限公司 | A kind of unilateral gate |
| CN111779806A (en) * | 2020-08-01 | 2020-10-16 | 山东锐拓泵业有限公司 | A reciprocating pump transmission |
| CN112573119A (en) * | 2019-09-29 | 2021-03-30 | 中烟机械技术中心有限责任公司 | Reciprocating motion device |
-
2007
- 2007-09-29 CN CNU200720043957XU patent/CN201100380Y/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101813170A (en) * | 2009-10-16 | 2010-08-25 | 北京中清能发动机技术有限公司 | Mechanism for mutual conversion between reciprocating motion and rotating motion, part and device thereof |
| CN101813170B (en) * | 2009-10-16 | 2012-01-11 | 北京中清能发动机技术有限公司 | Mechanism for mutual conversion between reciprocating motion and rotating motion, part and device thereof |
| CN106809452A (en) * | 2017-04-16 | 2017-06-09 | 浙江江南制药机械有限公司 | A kind of roller plate blister packaging machine is horizontally-opposed to be punched and beats lot number integrated device |
| CN107598036A (en) * | 2017-11-01 | 2018-01-19 | 王流洋 | A kind of double cut-out station bar croppers |
| CN110397382A (en) * | 2018-07-27 | 2019-11-01 | 襄阳市思想机电科技有限公司 | A kind of multi-connecting-rod mechanism |
| CN110397381A (en) * | 2018-07-27 | 2019-11-01 | 襄阳市思想机电科技有限公司 | A kind of unilateral gate |
| CN110397382B (en) * | 2018-07-27 | 2024-04-26 | 襄阳市思想机电科技有限公司 | Multi-link mechanism |
| CN110397381B (en) * | 2018-07-27 | 2024-04-26 | 襄阳市思想机电科技有限公司 | One-way door |
| CN109162894A (en) * | 2018-08-07 | 2019-01-08 | 中国石油大学(北京) | Sulfur resistive compressor |
| CN109826777A (en) * | 2019-01-29 | 2019-05-31 | 四川金星清洁能源装备股份有限公司 | Two-way crosshead transmission mechanism for Reciprocting piston compressor |
| CN112573119A (en) * | 2019-09-29 | 2021-03-30 | 中烟机械技术中心有限责任公司 | Reciprocating motion device |
| CN111779806A (en) * | 2020-08-01 | 2020-10-16 | 山东锐拓泵业有限公司 | A reciprocating pump transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Jiangsu Shuangda Pump & Valve Co., Ltd. Assignor: Jiangsu Shuangda Membrane Pump Manufacture Co., Ltd.|Chen Gensheng Contract fulfillment period: 2009.5.14 to 2017.5.14 Contract record no.: 2009320000924 Denomination of utility model: Line reciprocating joint machine for opposite crank sliding block Granted publication date: 20080813 License type: Exclusive license Record date: 20090514 |
|
| LIC | Patent licence contract for exploitation submitted for record |
Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2009.5.14 TO 2017.5.14; CHANGE OF CONTRACT Name of requester: JIANGSU SHUANGDA VALVE GROUP CO.,LTD. Effective date: 20090514 |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080813 Termination date: 20120929 |