CN201891482U - Diesel engine cooling and circulating system - Google Patents
Diesel engine cooling and circulating system Download PDFInfo
- Publication number
- CN201891482U CN201891482U CN2010202992776U CN201020299277U CN201891482U CN 201891482 U CN201891482 U CN 201891482U CN 2010202992776 U CN2010202992776 U CN 2010202992776U CN 201020299277 U CN201020299277 U CN 201020299277U CN 201891482 U CN201891482 U CN 201891482U
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- heat exchanger
- major cycle
- diesel engine
- water pump
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Abstract
The utility model discloses a diesel engine cooling and circulating system comprising circulating water paths formed by connection pipes and channels directly arranged in a machine body, wherein the circulating water paths include a large circulating path provided with a heat exchanger and a small circulating path provided with no heat exchanger. Coolant, after running through the machine body and a cylinder cover, either flows directly to a water pump via the small circulating path, or flows to the pump after cooled via the larger circulating path. The circulating water paths are provided with a thermoregulator for controlling the opening and closing of the large circulating path and the small circulating path. A large circulation direct path in parallel water route connection with the heat exchanger is provided on the large circulating path so that partial coolant can directly flow back to the water pump without passing through the heat exchanger. Compared with the prior art, a large circulation direct path in parallel water route connection with the heat exchanger is added on the large circulating path, which effectively prevents the cavitation and ensures the cooling function of an entire machine.
Description
Technical field
The utility model relates to a kind of diesel engine cooling recirculation system, relates in particular to a kind of marine diesel engine cooling recirculation system.
Background technique
Diesel engine is in the process of work, and positions such as body, cylinder cap, machine oil cooler can produce a lot of heats.For guarantee that these positions work in suitable temperature range, prevent that temperature is too high and influence the performance of diesel engine performance, need carry out suitable cooling to these positions.The diesel engine cooling recirculation system is exactly a coolant flow pipe-line system that is used to cool off these positions.Reasonably diesel engine cooling recirculation system structure plays a crucial effects for the performance of diesel engine performance.
In the marine diesel engine cooling recirculation system, be furnished with major cycle path and short circle path usually, and use thermoregulator to change circulating path.Thermoregulator plays the effect of a switch, and when engine coolant temperature was low, thermoregulator was in the short circle working state, and cooling liquid directly is back to water pump after cylinder cap flows out, and stops cooling liquid to flow to heat exchanger, reaches the effect of rapid warming-up with this; When engine coolant temperature was higher, thermoregulator was in the major cycle working state, cooling liquid then flow to heat exchanger and dispel the heat, and the cooling liquid behind radiating and cooling enters water pump.
The defective that existing diesel engine cooling recirculation system exists is, the cooling recirculation system device cavitates easily, itself and cavitation erosion can cause the erosion corrosion of water pump vane, even cause that impeller breaks, surface layer peeling, have a strong impact on the complete machine refrigerating function.
The model utility content
The technical problems to be solved in the utility model is to provide a kind of diesel engine cooling recirculation system, and this cooling recirculation system can be avoided the generation of cavitating effectively, and then guarantees the complete machine cooling effect.
For solving the problems of the technologies described above, the utility model provides a kind of diesel engine cooling recirculation system with following structure:
A kind of diesel engine cooling recirculation system, comprise by connecting tube and directly be arranged at the circulation waterway that the passage in the body constitutes, described circulation waterway comprises the major cycle path that heat exchanger is installed and the short circle path of uneasy assembling heat exchanger, the cooling liquid body of flowing through, behind the cylinder cap, both can directly get back to water pump through the short circle path, also can obtain being back to water pump after the cooling through the major cycle path, the thermoregulator that is used to control major cycle path and short circle channel opening and closing is installed on the described circulation waterway, described major cycle path is provided with a major cycle direct path in parallel with the heat exchanger water route, makes last minute cooling liquid of major cycle path can directly be back to water pump without heat exchanger.
Preferably, described major cycle path is provided with second water pump.
Preferably, on the described circulation waterway a plurality of water pumps are installed.
Preferably, on the described major cycle path swelling water tank is installed, is used for cooling system is replenished cooling liquid.
Preferably, described major cycle path is by way of machine oil cooler, so that machine oil cooler is cooled off.
Preferably, described major cycle path is by way of intercooler, so that intercooler is cooled off.
Compared with prior art, the utility model is by being provided with a major cycle direct path in parallel with the heat exchanger water route, avoids the generation of cavitating effectively, and then guaranteed the complete machine refrigerating function.
Description of drawings
Fig. 1 is the water route structural representation of the utility model embodiment diesel engine cooling recirculation system, and the direction of arrow wherein is water (flow) direction.
Embodiment
Below in conjunction with accompanying drawing, embodiment of the present utility model is described in detail, but is to be understood that protection domain of the present utility model is not subjected to the restriction of embodiment.
As shown in Figure 1, this diesel engine cooling recirculation system, comprise by connecting tube and be arranged at the circulation waterway that the passage in the body constitutes, first water pump that is used to provide circulation power is installed on the described circulation waterway, cooling liquid is behind flow through under the pressure of first water pump body, cylinder cap, both can directly get back to first water pump, and also can flow to heat exchanger through the D among the major cycle path B along separate routes and obtain being back to first water pump after the cooling, thereby constitute the water route circulation through short circle path A.Described major cycle path B is provided with a C path in parallel with D path water route, makes last minute cooling liquid of B path can directly be back to first water pump without heat exchanger.The thermoregulator that is used to control major cycle path B and short circle path A switching is installed on the described circulation waterway.
In the described cooling recirculation system, when described coolant temperature was lower than the unlatching temperature of thermoregulator, under the control of thermoregulator, cooling liquid flow to a node through the A road, and was back to the influent side of first water pump.Just open temperature but when being lower than the standard-sized sheet temperature when what described coolant temperature was higher than thermoregulator, cooling liquid branches to A road and B road behind thermoregulator, after flowing to a node, the cooling liquid on A road promptly is back to the influent side of first water pump, after the cooling liquid on B road flow to the b node, then be split into C road and D road, distribute to of the structure actual internal area decision of the coolant rate general proportions on C road and D road through the b node according to actual design; Cooling liquid on the C road directly is back to first water pump, when described C road can guarantee the first water pump operation rotating speed moment rising, cooling liquid can be fast through the C road to a node, and be back to first water pump, satisfy the rapid recharge to inflow when improving of first pump rotary speed moment with this, avoid causing cavitating because of saturated vapor pressure reduces in the whole cooling system device, prove through severe test, this cavitation erosion can cause the erosion corrosion of water pump vane, even cause that impeller breaks, surface layer peeling, have a strong impact on the complete machine refrigerating function.The described cooling liquid that branches to the D road through sea water and fresh water heat exchanger, second water pump, intercooler, machine oil cooler behind the E road, merge into the F road with the cooling liquid that branches to the C road before at the c node, and the cooling liquid on final and A road after converging, a node is back to the influent side of first water pump.When described coolant temperature was higher than the standard-sized sheet temperature of thermoregulator, cooling liquid was through all flowing to the B road behind the thermoregulator, and was divided into above-mentioned C road and the D road is back to first water pump at last.
On above-mentioned D road, second water pump is installed, thereby reduced the on-way resistance of cooling system, improved cooling effectiveness, reduced performance requirement to water pump, and guaranteed that cooling system has higher reliability, when a water pump broke down, another water pump still can provide the pump outlet capacity of certain intensity.
After the cooling liquid of thermoregulator of flowing through reaches and opens temperature, cooling liquid then participates in flowing in two cover circulation loops simultaneously, no matter thermoregulator is all opened still part unlatching, all some directly is back to the first water pump influent side to cooling liquid after thermolator base flows out, helps shortening the warm-up period of complete machine and continues to provide suitable intensity of cooling to complete machine.
The utility model cooling system circulatory system is applicable to marine engine, hull auxiliaries, land generator set, water tower formula cooling power station.
More than disclosed only be a specific embodiment of the present utility model, still, the utility model is not limited thereto, any those skilled in the art can think variation all should fall into protection domain of the present utility model.
Claims (5)
1. diesel engine cooling recirculation system, comprise by connecting tube and directly be arranged at the circulation waterway that the passage in the body constitutes, described circulation waterway comprises the major cycle path that heat exchanger is installed and the short circle path of uneasy assembling heat exchanger, the cooling liquid body of flowing through, behind the cylinder cap, both can directly get back to water pump through the short circle path, also can obtain being back to water pump after the cooling through the major cycle path, the thermoregulator that is used to control major cycle path and short circle channel opening and closing is installed on the described circulation waterway, it is characterized in that, described major cycle path is provided with a major cycle direct path in parallel with the heat exchanger water route, makes last minute cooling liquid of major cycle path can directly be back to water pump without heat exchanger.
2. diesel engine cooling recirculation system according to claim 1 is characterized in that, a plurality of water pumps are installed on the described circulation waterway.
3. diesel engine cooling recirculation system according to claim 2 is characterized in that, on the described major cycle path swelling water tank is installed, and is used for cooling system is replenished cooling liquid.
4. diesel engine cooling recirculation system according to claim 3 is characterized in that, described major cycle path is by way of machine oil cooler, so that machine oil cooler is cooled off.
5. diesel engine cooling recirculation system according to claim 4 is characterized in that, described major cycle path is by way of intercooler, so that intercooler is cooled off.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202992776U CN201891482U (en) | 2010-08-17 | 2010-08-17 | Diesel engine cooling and circulating system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202992776U CN201891482U (en) | 2010-08-17 | 2010-08-17 | Diesel engine cooling and circulating system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201891482U true CN201891482U (en) | 2011-07-06 |
Family
ID=44220958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010202992776U Expired - Fee Related CN201891482U (en) | 2010-08-17 | 2010-08-17 | Diesel engine cooling and circulating system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201891482U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102723813A (en) * | 2012-06-18 | 2012-10-10 | 苏州腾辉环保科技有限公司 | Novel steam turbine generator cooling system |
| CN103573379A (en) * | 2013-10-12 | 2014-02-12 | 广西玉柴机器股份有限公司 | Water type heat exchanger for ship turbine |
| CN103573380A (en) * | 2013-10-17 | 2014-02-12 | 北京北方华德尼奥普兰客车股份有限公司 | Passenger car rear engine cooling system with air bubble purification function |
| CN103615302A (en) * | 2013-12-05 | 2014-03-05 | 安徽江淮汽车股份有限公司 | Cooling system of engine |
| CN105275571A (en) * | 2015-11-09 | 2016-01-27 | 安徽江淮汽车股份有限公司 | Automobile cooling water circulation control system and method and automobile |
| CN105332783A (en) * | 2015-11-18 | 2016-02-17 | 河北华北柴油机有限责任公司 | Integrated axial symmetrical cooling system of water-cooled diesel engine |
| CN106460664A (en) * | 2014-04-08 | 2017-02-22 | 鲍尔法斯有限责任公司 | Gas turbine efficiency and regulation speed improvements using supplementary air system |
| CN110513183A (en) * | 2019-09-28 | 2019-11-29 | 河南柴油机重工有限责任公司 | A kind of marine diesel dual cycle cooling system |
-
2010
- 2010-08-17 CN CN2010202992776U patent/CN201891482U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102723813A (en) * | 2012-06-18 | 2012-10-10 | 苏州腾辉环保科技有限公司 | Novel steam turbine generator cooling system |
| CN103573379A (en) * | 2013-10-12 | 2014-02-12 | 广西玉柴机器股份有限公司 | Water type heat exchanger for ship turbine |
| CN103573380A (en) * | 2013-10-17 | 2014-02-12 | 北京北方华德尼奥普兰客车股份有限公司 | Passenger car rear engine cooling system with air bubble purification function |
| CN103573380B (en) * | 2013-10-17 | 2015-10-21 | 北京北方华德尼奥普兰客车股份有限公司 | A kind of passenger vehicle rear engine cooling system with bubble purification function |
| CN103615302A (en) * | 2013-12-05 | 2014-03-05 | 安徽江淮汽车股份有限公司 | Cooling system of engine |
| CN103615302B (en) * | 2013-12-05 | 2015-09-09 | 安徽江淮汽车股份有限公司 | A kind of cooling system of motor |
| CN106460664A (en) * | 2014-04-08 | 2017-02-22 | 鲍尔法斯有限责任公司 | Gas turbine efficiency and regulation speed improvements using supplementary air system |
| CN106460664B (en) * | 2014-04-08 | 2021-03-12 | 鲍尔法斯有限责任公司 | Gas turbine efficiency and turndown speed improvements using supplemental air systems |
| CN105275571A (en) * | 2015-11-09 | 2016-01-27 | 安徽江淮汽车股份有限公司 | Automobile cooling water circulation control system and method and automobile |
| CN105332783A (en) * | 2015-11-18 | 2016-02-17 | 河北华北柴油机有限责任公司 | Integrated axial symmetrical cooling system of water-cooled diesel engine |
| CN110513183A (en) * | 2019-09-28 | 2019-11-29 | 河南柴油机重工有限责任公司 | A kind of marine diesel dual cycle cooling system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110706 Termination date: 20150817 |
|
| EXPY | Termination of patent right or utility model |