CN210669791U - Motor cooling liquid spraying circulating system for compressor - Google Patents
Motor cooling liquid spraying circulating system for compressor Download PDFInfo
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- CN210669791U CN210669791U CN201922053758.2U CN201922053758U CN210669791U CN 210669791 U CN210669791 U CN 210669791U CN 201922053758 U CN201922053758 U CN 201922053758U CN 210669791 U CN210669791 U CN 210669791U
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Abstract
The utility model discloses a motor cooling hydrojet circulation system for compressor, including oil separator, flash vessel, evaporimeter, heat exchanger, the air inlet of oil separator communicates with first pipeline, the oil separator communicates the flash vessel through the second pipeline, the gas vent of oil separator communicates with the third pipeline; the liquid outlet of the flash evaporator is connected with the liquid inlet of the evaporator through a fourth pipeline; an air outlet of the evaporator is communicated with the heat exchanger through a fifth pipeline, and a liquid outlet of the evaporator is communicated with a sixth pipeline; and a liquid outlet of the heat exchanger is communicated with a liquid inlet of the evaporator through a seventh pipeline, an air outlet of the heat exchanger is communicated with an eighth pipeline, and an air inlet of the heat exchanger is communicated with a ninth pipeline. The utility model discloses a cooling circulation system improves the cooling capacity of device, and effective control high temperature gas backward flow prevents that the motor temperature rise is too high, reduces the mechanical deformation that the temperature rise produced, promotes high-pressure level mass flow simultaneously, improves whole refrigeration cycle's efficiency.
Description
Technical Field
The utility model relates to a motor cooling technical field of compressor, more specifically the utility model relates to a motor cooling hydrojet circulation system for compressor that says so.
Background
Energy conservation and environmental protection become the development direction of all mankind, how to save energy and reduce emission in the production of pharmaceutical and chemical industries in China at present, and the improvement of the competitiveness of enterprise products becomes the primary target, and the development of the industry of enterprises is also related.
However, in the medical and chemical fields, it is difficult to avoid using a screw compressor, in which a pair of helical male and female rotors are mounted in a cylinder, and both rotors have several concave teeth and rotate in opposite directions. The clearance between the rotors and between the machine shell and the rotors is only 5-10 wires, the main rotor is driven by an engine or a motor, and the other rotor is driven by an oil film formed by oil injection of the main rotor or driven by synchronous gears at the ends of the main rotor and the concave rotor.
The length and diameter of the rotor determine the displacement (flow) and discharge pressure of the compressor, and the longer the rotor, the higher the pressure; the larger the rotor diameter, the greater the flow.
However, the processing precision of the small-diameter screw compressor is worse than that of the large-diameter screw compressor due to the size limitation of the screw, because the temperature rise of the motor caused by high-temperature exhaust backflow is too high when the solvent is evaporated in the production process, and the allowable high-temperature working value of the motor of the compressor is lower, so that the service life span of the compressor is shortened, the use cost is too high, and the safety of the equipment is extremely low.
For the small-diameter screw compressor, although the temperature of the motor can be effectively reduced by directly cooling the small-diameter screw compressor by using the refrigerant liquid of the condenser, the small-diameter screw compressor needs higher cooling capacity to prevent adverse effects on the small-diameter screw compressor caused by high-temperature gas backflow.
SUMMERY OF THE UTILITY MODEL
In order to solve the problem, the utility model discloses a motor cooling hydrojet circulation system for compressor to minor diameter screw compressor, sets up the subcooling link on motor hydrojet circulation, with its subcooling to very low temperature, makes the cooling capacity of its hydrojet very improve, and the high-temperature gas reflux of effective control prevents that the motor temperature rise is too high, reduces the mechanical deformation that the temperature rise produced, promotes high-pressure level mass flow simultaneously, improves whole refrigeration cycle's efficiency.
In order to achieve the above purpose, the utility model provides a following technical scheme:
a motor cooling liquid spraying circulation system for a compressor comprises the compressor, and the compressor comprises an oil separator, a flash evaporator, an evaporator and a heat exchanger, wherein a gas inlet of the oil separator is communicated with a first pipeline so that fluid can be introduced into the oil separator, the oil separator is communicated with the flash evaporator through a second pipeline so that liquid can be introduced into the flash evaporator from the oil separator, and a gas outlet of the oil separator is communicated with a third pipeline so that gas can be discharged from the oil separator;
the liquid outlet of the flash evaporator is connected with the liquid inlet of the evaporator through a fourth pipeline, so that fluid is introduced into the evaporator from the flash evaporator;
an air outlet of the evaporator is communicated with the heat exchanger through a fifth pipeline, so that air is introduced into the heat exchanger, and a liquid outlet of the evaporator is communicated with a sixth pipeline, so that liquid is discharged from the evaporator;
and a liquid outlet of the heat exchanger is communicated with a liquid inlet of the evaporator through a seventh pipeline, so that liquid in the heat exchanger is introduced into the evaporator, an air outlet of the heat exchanger is communicated with an eighth pipeline and used for discharging gas in the heat exchanger, and an air inlet of the heat exchanger is communicated with a ninth pipeline, so that fluid is introduced into the heat exchanger.
As a further description of the above technical solution:
the oil-gas separation unit comprises a compressor, an oil separator, a condenser and a flash evaporator, wherein the compressor, the oil separator, the condenser and the flash evaporator are sequentially connected.
As a further description of the above technical solution:
the seventh pipeline is communicated with the fourth pipeline, a three-way pipe is arranged at the joint of the seventh pipeline and the fourth pipeline, and the three-way pipe is only communicated with the evaporator, the heat exchanger and the flash evaporator.
As a further description of the above technical solution:
the heat exchanger is a dividing wall type heat exchanger or a mixed heat exchanger.
As a further description of the above technical solution:
the cooling medium in the heat exchanger is Freon.
As a further description of the above technical solution:
when the heat exchanger is a dividing wall type heat exchanger, the fifth pipeline is communicated with the eighth pipeline and only has one fluid passage, and the seventh pipeline is communicated with the ninth pipeline and only has one fluid passage.
As a further description of the above technical solution:
when the heat exchanger is a hybrid heat exchanger, pipelines connected to the heat exchanger are not mutually connected.
As a further description of the above technical solution:
and the seventh pipeline and the fourth pipeline are respectively provided with a control valve assembly.
As a further description of the above technical solution:
the control valve assembly is an electromagnetic valve, a manual ball valve and an expansion valve.
To sum up, owing to adopted above-mentioned technical scheme, the beneficial effects of the utility model are that:
1. aiming at the defects of the small-diameter screw compressor, a supercooling link is arranged on the spray circulation of the motor to supercool the spray to a very low temperature, so that the cooling capacity of the spray is greatly improved.
2. The backflow of high-temperature gas can be effectively controlled, the motor is prevented from being overhigh in temperature rise, and mechanical deformation caused by the temperature rise is reduced.
3. The high-pressure-level mass flow is improved, and the efficiency of the whole refrigeration cycle is improved.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 is a schematic structural diagram of a motor cooling liquid spray circulation system for a compressor according to the present invention;
FIG. 2 is a schematic view of a fluid path;
FIG. 3 is an enlarged view of FIG. 2A;
fig. 4 is a schematic view of a fluid path in which the present system is applied.
The labels in the figure are: 1-oil separator, 2-flash evaporator, 3-evaporator, 4-heat exchanger, 5-first pipeline, 6-second pipeline, 7-third pipeline, 8-fourth pipeline, 9-fifth pipeline, 10-sixth pipeline, 11-seventh pipeline, 12-eighth pipeline, and 13-ninth pipeline.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the invention, i.e., the described embodiments are only some, but not all embodiments of the invention. The components of embodiments of the present invention, as generally described and illustrated in the figures herein, may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the accompanying drawings, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. Based on the embodiment of the present invention, all other embodiments obtained by the person skilled in the art without creative work belong to the protection scope of the present invention.
It is noted that relational terms such as "first" and "second," and the like, may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
The features and properties of the present invention are described in further detail below with reference to examples.
Example 1
When a compressor is used in the medical and chemical fields at present, a screw compressor is difficult to avoid, the length and the diameter of a rotor in the screw compressor determine the displacement (flow) and the exhaust pressure of the compressor, and the longer the rotor is, the higher the pressure is; the larger the rotor diameter, the larger the flow;
however, the processing precision of the small-diameter screw compressor is worse than that of the large-diameter screw compressor due to the size limitation of the screw, because the temperature rise of the motor caused by high-temperature exhaust backflow is too high when the solvent is evaporated in the production process, and the allowable high-temperature working value of the motor of the compressor is lower, so that the service life span of the compressor is shortened, the use cost is too high, and the safety of the equipment is extremely low;
therefore, a motor cooling liquid spraying circulation system for a compressor is developed, and comprises an oil separator 1, a flash evaporator 2, an evaporator 3 and a heat exchanger 4, wherein an air inlet of the oil separator 1 is communicated with a first pipeline 5 so that fluid can pass into the oil separator 1, the oil separator 1 is communicated with the flash evaporator 2 through a second pipeline 6 so that liquid can pass into the flash evaporator 2 from the oil separator 1, and an air outlet of the oil separator 1 is communicated with a third pipeline 7 so that gas can be discharged from the oil separator 1;
a liquid outlet of the flash evaporator 2 is connected with a liquid inlet of the evaporator 3 through a fourth pipeline 8, so that fluid is introduced into the evaporator 3 from the flash evaporator 2;
the exhaust port of the evaporator 3 is communicated with a heat exchanger 4 through a fifth pipeline 9, so that gas is introduced into the heat exchanger 4, and the liquid outlet of the evaporator 3 is communicated with a sixth pipeline 10, so that liquid is discharged from the evaporator 3;
a liquid outlet of the heat exchanger 4 is communicated with a liquid inlet of the evaporator 3 through a seventh pipeline 11, so that liquid in the heat exchanger 4 is introduced into the evaporator 3, an air outlet of the heat exchanger 4 is communicated with an eighth pipeline 12 for discharging gas in the heat exchanger 4, and an air inlet of the heat exchanger 4 is communicated with a ninth pipeline 13, so that fluid is introduced into the heat exchanger 4.
The working principle of the embodiment is as follows:
when the gas-liquid mixture with high pressure and high temperature is introduced into the gas inlet of the oil separator 1 from the first pipeline 5, the oil separator 1 introduces the mixed liquid of oil and freon into the flash evaporator 2 from the second pipeline 6, the gas is discharged from the oil separator 1 from the third pipeline 7, the flash evaporator 2 separates the liquid freon and the oil, the fourth pipeline 8 conveys the liquid freon into the evaporator 3, the liquid freon is changed into gaseous freon in the evaporator 3, so that the heat absorption effect is achieved, the gaseous freon is introduced into the heat exchanger 4 through the fifth pipeline 9, the gaseous freon becomes a heat exchange medium in the heat exchanger 4, the high-temperature gas generated in the device by the gas discharged from the third pipeline 7 flows back and is introduced into the heat exchanger 4 through the ninth pipeline 13, the freon gasified in the evaporator 3 is introduced into the heat exchanger 4 through the fifth pipeline 9, the eighth pipeline 12 discharges the gasified freon, the gasified freon cools and cools the high-temperature return gas in the heat exchanger 4, so that the high-temperature return gas is liquefied, the liquefied high-temperature return gas flows into the evaporator 3 through the seventh pipeline 11, and the liquefied high-temperature return gas is discharged from the evaporator 3 through the sixth pipeline 10;
further, in order to save the pipe distribution cost, the seventh pipeline 11 is communicated with the fourth pipeline 8, the joint of the seventh pipeline 11 and the fourth pipeline 8 is a three-way pipe, and the three-way pipe is only communicated with the evaporator 3, the heat exchanger 4 and the flash evaporator 2;
preferably, the heat exchanger 4 is a dividing wall type heat exchanger or a hybrid heat exchanger;
when the heat exchanger 4 is a dividing wall type heat exchanger, the fifth pipeline 9 is communicated with the eighth pipeline 12 and only has one fluid passage, the seventh pipeline 13 is communicated with the ninth pipeline 13 and only has one fluid passage, gaseous Freon and high-temperature return gas are not directly contacted and mixed in the heat exchanger 4, after the heat absorbed Freon is liquefied, the liquefied Freon flows back to the evaporator 3 through the fifth pipeline 9 to be gasified again, the non-liquefied Freon is continuously discharged through the eighth pipeline 12, the ninth pipeline 13 introduces the high-temperature return gas into the heat exchanger 4, after the cooling of the gaseous Freon, the liquefied high-temperature return gas flows into the evaporator 3 through the seventh pipeline 11, and the liquefied high-temperature return gas is discharged out of the evaporator 3 through the sixth pipeline 10;
when the heat exchanger 4 is a hybrid heat exchanger, the pipelines connected to the heat exchanger 4 are not connected to each other, the gasified freon is introduced into the heat exchanger 4, and then mixed with the high-temperature return gas introduced into the heat exchanger 4 from the ninth pipeline 13, the liquefied freon and the liquefied high-temperature return gas are introduced into the evaporator 3 from the seventh pipeline 11, the liquefied freon is gasified again in the evaporator 3, the gasified freon is introduced into the heat exchanger 4 again for heat exchange, the liquefied high-temperature return gas is discharged from the evaporator 3 from the sixth pipeline 10, and the freon which is not liquefied in the heat exchanger 4 is continuously discharged from the eighth pipeline 12;
more practically, the seventh pipeline 11 and the fourth pipeline 8 are respectively provided with a control valve assembly; the control valve assembly is an electromagnetic valve, a manual ball valve and an expansion valve;
whether the passage of the seventh pipeline 11 and the ninth pipeline 13 is opened or not can be controlled by the electromagnetic valve, the Freon passing through is changed into low-temperature low-pressure wet steam by the expansion valve, so that the wet steam is better gasified in the evaporator 3, and the expansion valve can more effectively reduce the temperature and the pressure of high-temperature return gas, so that the insufficient liquefaction of the high-temperature return gas is fully prevented.
In practical application, the eighth pipeline 12 is connected with a compressor, and after the gasified Freon is introduced into the compressor, the cooling efficiency of the compressor can be effectively improved;
therefore, a supercooling link is arranged on the liquid spraying circulation of the motor aiming at the small-diameter screw compressor, the liquid spraying circulation is supercooled to a very low temperature, the cooling capacity of the liquid spraying is greatly improved, the backflow of high-temperature gas is effectively controlled, the overhigh temperature rise of the motor is prevented, the mechanical deformation caused by the temperature rise is reduced, the high-pressure-level mass flow is improved, and the efficiency of the whole refrigeration circulation is improved.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not intended to limit the present invention, and any modifications, equivalent replacements, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.
Claims (8)
1. A motor cooling hydrojet circulation system for compressor which characterized in that:
the device comprises an oil separator (1), a flash evaporator (2), an evaporator (3) and a heat exchanger (4), wherein an air inlet of the oil separator (1) is communicated with a first pipeline (5) so that fluid can be introduced into the oil separator (1), the oil separator (1) is communicated with the flash evaporator (2) through a second pipeline (6) so that liquid can be introduced into the flash evaporator (2) from the oil separator (1), and an air outlet of the oil separator (1) is communicated with a third pipeline (7) so that gas can be discharged from the oil separator (1);
a liquid outlet of the flash evaporator (2) is connected with a liquid inlet of the evaporator (3) through a fourth pipeline (8), so that the fluid is introduced into the evaporator (3) from the flash evaporator (2);
the exhaust port of the evaporator (3) is communicated with a heat exchanger (4) through a fifth pipeline (9) so that gas is introduced into the heat exchanger (4), and the liquid outlet of the evaporator (3) is communicated with a sixth pipeline (10) so that liquid is discharged from the evaporator (3);
a liquid outlet of the heat exchanger (4) is communicated with a liquid inlet of the evaporator (3) through a seventh pipeline (11), so that liquid in the heat exchanger (4) is introduced into the evaporator (3), an exhaust port of the heat exchanger (4) is communicated with an eighth pipeline (12) and used for exhausting gas in the heat exchanger (4), and an air inlet of the heat exchanger (4) is communicated with a ninth pipeline (13) so that fluid is introduced into the heat exchanger (4).
2. A motor-cooled spray circulation system for a compressor, as claimed in claim 1, wherein: the seventh pipeline (11) is communicated with the fourth pipeline (8), the joint of the seventh pipeline (11) and the fourth pipeline (8) is a three-way pipe, and the three-way pipe is only communicated with the evaporator (3), the heat exchanger (4) and the flash evaporator (2).
3. A motor-cooled spray circulation system for a compressor, as claimed in claim 1, wherein: the heat exchanger (4) is a dividing wall type heat exchanger or a mixed type heat exchanger.
4. A motor-cooled spray circulation system for a compressor, as claimed in claim 1, wherein: and the cooling medium in the heat exchanger (4) is Freon.
5. A motor-cooled spray circulation system for a compressor, as claimed in claim 3, wherein: when the heat exchanger (4) is a dividing wall type heat exchanger, the fifth pipeline (9) is communicated with the eighth pipeline (12) and only has one fluid passage, and the seventh pipeline is communicated with the ninth pipeline (13) and only has one fluid passage.
6. A motor-cooled spray circulation system for a compressor, as claimed in claim 3, wherein: when the heat exchanger (4) is a hybrid heat exchanger, pipelines connected to the heat exchanger (4) are not connected with each other.
7. A motor-cooled spray circulation system for a compressor, as claimed in claim 1, wherein: and the seventh pipeline (11) and the fourth pipeline (8) are respectively provided with a control valve assembly.
8. A motor-cooled spray circulation system for a compressor, as claimed in claim 7, wherein: the control valve assembly is an electromagnetic valve, a manual ball valve and an expansion valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922053758.2U CN210669791U (en) | 2019-11-25 | 2019-11-25 | Motor cooling liquid spraying circulating system for compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922053758.2U CN210669791U (en) | 2019-11-25 | 2019-11-25 | Motor cooling liquid spraying circulating system for compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210669791U true CN210669791U (en) | 2020-06-02 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201922053758.2U Expired - Fee Related CN210669791U (en) | 2019-11-25 | 2019-11-25 | Motor cooling liquid spraying circulating system for compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210669791U (en) |
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2019
- 2019-11-25 CN CN201922053758.2U patent/CN210669791U/en not_active Expired - Fee Related
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200602 Termination date: 20211125 |
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| CF01 | Termination of patent right due to non-payment of annual fee |