CN106801734A - A kind of gas gear - Google Patents
A kind of gas gear Download PDFInfo
- Publication number
- CN106801734A CN106801734A CN201610983272.7A CN201610983272A CN106801734A CN 106801734 A CN106801734 A CN 106801734A CN 201610983272 A CN201610983272 A CN 201610983272A CN 106801734 A CN106801734 A CN 106801734A
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- China
- Prior art keywords
- radial flow
- displacement
- gas
- ratio
- impeller pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/04—Combined pump-turbine units
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rotary Pumps (AREA)
Abstract
Description
技术领域technical field
本发明涉及动力与传动领域，尤其涉及一种气体变速机构。The invention relates to the field of power and transmission, in particular to a gas transmission mechanism.
背景技术Background technique
如果能够发明一种能够提高动力单元的动力性和负荷响应能力的系统，将有效提高动力单元的适用性。因此，需要发明一种新的气体变速机构。If a system that can improve the dynamic performance and load response capability of the power unit can be invented, the applicability of the power unit will be effectively improved. Therefore, need to invent a kind of new gas transmission mechanism.
发明内容Contents of the invention
为了解决上述问题，本发明提出的技术方案如下：In order to solve the above problems, the technical scheme proposed by the present invention is as follows:
本发明的气体变速机构，包括径流气体叶轮泵和径流透平，所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值在0.7以上1.3以下，所述径流气体叶轮泵的排量和所述径流透平的排量不等。The gas transmission mechanism of the present invention includes a radial flow gas impeller pump and a radial flow turbine, the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine is between 0.7 and 1.3, and the discharge of the radial flow gas impeller pump The volume varies from the displacement of the radial flow turbine.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的两倍以上。Further optionally, the displacement of the radial flow turbine is more than twice the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值在0.8以上1.2以下。Further optionally, the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine is not less than 0.8 and not more than 1.2.
进一步可选择地，使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值为0.9以上1.1以下。Further optionally, the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine is 0.9 to 1.1.
进一步可选择地，使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值为1.0。Further optionally, the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine is 1.0.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的三倍以上。Further optionally, the displacement of the radial flow turbine is more than three times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的四倍以上。Further optionally, the displacement of the radial flow turbine is more than four times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的五倍以上。Further optionally, the displacement of the radial flow turbine is more than five times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的六倍以上。Further optionally, the displacement of the radial flow turbine is more than six times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的七倍以上。Further optionally, the displacement of the radial flow turbine is more than seven times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的八倍以上。Further optionally, the displacement of the radial flow turbine is more than eight times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的九倍以上。Further optionally, the displacement of the radial flow turbine is more than nine times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十倍以上。Further optionally, the displacement of the radial flow turbine is more than ten times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十一倍以上。Further optionally, the displacement of the radial flow turbine is more than eleven times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十二倍以上。Further optionally, the displacement of the radial flow turbine is more than twelve times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十三倍以上。Further optionally, the displacement of the radial flow turbine is more than thirteen times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十四倍以上。Further optionally, the displacement of the radial flow turbine is more than fourteen times the displacement of the radial flow gas impeller pump.
进一步可选择地，使所述径流透平的排量是所述径流气体叶轮泵的排量的十五倍以上。Further optionally, the displacement of the radial flow turbine is more than fifteen times the displacement of the radial flow gas impeller pump.
本发明中，应根据动力和传动领域的公知技术，在必要的地方设置必要的部件、单元或系统等。In the present invention, necessary components, units or systems should be provided where necessary according to known technologies in the field of power and transmission.
本发明的有益效果如下:The beneficial effects of the present invention are as follows:
本发明所公开的气体变速机构能够有效地提高和改善应用其的动力装置或系统的动力性、适应性以及负荷响应能力。The gas transmission mechanism disclosed by the invention can effectively improve and improve the dynamic performance, adaptability and load response capability of the power device or system to which it is applied.
具体实施方式detailed description
实施例1Example 1
一种气体变速机构，包括径流气体叶轮泵和径流透平，所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值在0.7以上1.3以下，所述径流气体叶轮泵的排量和所述径流透平的排量不等。A gas speed change mechanism, comprising a radial flow gas impeller pump and a radial flow turbine, the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine is between 0.7 and 1.3, and the displacement of the radial flow gas impeller pump is And the displacement of the radial flow turbine is not equal.
实施例2Example 2
一种气体变速机构，在实施例1的基础上，进一步使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值在0.8以上1.2以下。A gas speed change mechanism, on the basis of Embodiment 1, further makes the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine not less than 0.8 and not more than 1.2.
实施例3Example 3
一种气体变速机构，在实施例1的基础上，进一步使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值为0.9以上1.1以下。A gas speed change mechanism, on the basis of Embodiment 1, further makes the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine be not less than 0.9 and not more than 1.1.
实施例4Example 4
一种气体变速机构，在实施例1的基础上，进一步使所述径流气体叶轮泵的压比与所述径流透平膨胀比的比值为1.0。A gas speed change mechanism, on the basis of Embodiment 1, further makes the ratio of the pressure ratio of the radial flow gas impeller pump to the expansion ratio of the radial flow turbine be 1.0.
实施例5Example 5
一种气体变速机构，在实施例1的基础上，进一步使所述径流透平的排量是所述径流气体叶轮泵的排量的两倍以上。A gas speed change mechanism, on the basis of Embodiment 1, further makes the displacement of the radial flow turbine more than twice the displacement of the radial flow gas impeller pump.
作为可变换的实施方式，本发明实施例5还可选择性地选择使所述径流透平的排量是所述径流气体叶轮泵的排量的三倍以上、四倍以上、五倍以上、六倍以上、七倍以上、八倍以上、九倍以上、十倍以上、十一倍以上、十二倍以上、十三倍以上、十四倍以上或十五倍以上。As a changeable implementation mode, in Embodiment 5 of the present invention, the displacement of the radial flow turbine can also be selectively selected to be more than three times, more than four times, more than five times, or more than the displacement of the radial flow gas impeller pump. More than six times, more than seven times, more than eight times, more than nine times, more than ten times, more than eleven times, more than twelve times, more than thirteen times, more than fourteen times or more than fifteen times.
显然，本发明不限于以上实施例，根据本领域的公知技术和本发明所公开的技术方案，可以推导出或联想出许多变型方案，所有这些变型方案，也应认为是本发明的保护范围。Obviously, the present invention is not limited to the above examples. According to the known technologies in the art and the technical solutions disclosed in the present invention, many variants can be deduced or associated, and all these variants should also be considered as the protection scope of the present invention.
Claims (6)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2015108316740 | 2015-11-25 | ||
| CN201510831674 | 2015-11-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106801734A true CN106801734A (en) | 2017-06-06 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610983272.7A Pending CN106801734A (en) | 2015-11-25 | 2016-11-09 | A kind of gas gear |
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| CN (1) | CN106801734A (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4301649A (en) * | 1979-08-24 | 1981-11-24 | General Motors Corporation | Single rotor engine with turbine exhausting to subatmospheric pressure |
| US20040068975A1 (en) * | 2002-07-29 | 2004-04-15 | Skowronski Mark Joseph | Kinetic energy turbine with recuperation |
| CN102562304A (en) * | 2012-02-09 | 2012-07-11 | 中煤科工集团重庆研究院 | Power generator of catalytic combustion gas turbine |
| DE102012012862A1 (en) * | 2012-06-28 | 2014-01-02 | Boge Kompressoren Otto Boge Gmbh & Co. Kg | Device for creating pressurized air or under pressure standing gas, has high pressure compressor provided with adjustable guide vanes that are alternately operated in direction and utilized as expansion machine in another direction |
| CN103790660A (en) * | 2013-01-29 | 2014-05-14 | 摩尔动力(北京)技术股份有限公司 | Ultimate temperature ratio engine |
| CN104234834A (en) * | 2013-08-07 | 2014-12-24 | 摩尔动力(北京)技术股份有限公司 | Turbine engine |
| DE102014000469A1 (en) * | 2014-01-16 | 2015-07-16 | Gea Refrigeration Germany Gmbh | screw compressors |
| CN104832287A (en) * | 2014-03-25 | 2015-08-12 | 摩尔动力(北京)技术股份有限公司 | Speed-volume turbine engine |
-
2016
- 2016-11-09 CN CN201610983272.7A patent/CN106801734A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4301649A (en) * | 1979-08-24 | 1981-11-24 | General Motors Corporation | Single rotor engine with turbine exhausting to subatmospheric pressure |
| US20040068975A1 (en) * | 2002-07-29 | 2004-04-15 | Skowronski Mark Joseph | Kinetic energy turbine with recuperation |
| CN102562304A (en) * | 2012-02-09 | 2012-07-11 | 中煤科工集团重庆研究院 | Power generator of catalytic combustion gas turbine |
| DE102012012862A1 (en) * | 2012-06-28 | 2014-01-02 | Boge Kompressoren Otto Boge Gmbh & Co. Kg | Device for creating pressurized air or under pressure standing gas, has high pressure compressor provided with adjustable guide vanes that are alternately operated in direction and utilized as expansion machine in another direction |
| CN103790660A (en) * | 2013-01-29 | 2014-05-14 | 摩尔动力(北京)技术股份有限公司 | Ultimate temperature ratio engine |
| CN104234834A (en) * | 2013-08-07 | 2014-12-24 | 摩尔动力(北京)技术股份有限公司 | Turbine engine |
| DE102014000469A1 (en) * | 2014-01-16 | 2015-07-16 | Gea Refrigeration Germany Gmbh | screw compressors |
| CN104832287A (en) * | 2014-03-25 | 2015-08-12 | 摩尔动力(北京)技术股份有限公司 | Speed-volume turbine engine |
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Application publication date: 20170606 |