CN105180491A - Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit - Google Patents
Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit Download PDFInfo
- Publication number
- CN105180491A CN105180491A CN201510669129.6A CN201510669129A CN105180491A CN 105180491 A CN105180491 A CN 105180491A CN 201510669129 A CN201510669129 A CN 201510669129A CN 105180491 A CN105180491 A CN 105180491A
- Authority
- CN
- China
- Prior art keywords
- oil
- valve
- pipeline
- pressure
- unit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a full-condition efficient evaporation cooled screw parallel-connection thermo-siphon flooded type low-medium-temperature water chilling unit and relates to the field of industrial refrigeration. The water chilling unit comprises a screw type compressor parallel machine unit, an oil-gas separator, an exhaust pressure sensor, an oil level switch, a lubricating oil temperature sensor, a thermo-siphon oil cooler, an oil temperature three-way self-operated regulating valve, an oil supply differential pressure self-operated regulating valve, an evaporation type condenser, a high-pressure liquid reservoir, an energy saver, a liquid level control type regulating valve, a thermo-siphon flooded type evaporator, a low-pressure recycling gas-liquid separator, a liquid level switch, an ejecting oil scavenger, an electric control box, relative pipelines, valves and gauges. By means of the system, the coefficient of performance (COP) of an industrial refrigerating unit can be increased by over 30%, the maintenance cost of the industrial refrigerating unit can be reduced by over 50%, and therefore the industrial refrigerating unit can operate more safely, more reliably and more stably.
Description
Technical field
The present invention relates to low-temperature cold water unit in full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type, be specially adapted to leaving water temperature low-temperature industrial refrigerating field in-100 DEG C ~ 0 DEG C.
Background technology
1. in the single compressor used in the market low-temperature industrial handpiece Water Chilling Units by one carry one-level oil gas divergence type semi-hermetic screw compressor, water-cooled condenser, dry evaporator, energy-saving appliance, a secondary oil separator (without oil storage function) form, in this single compressor, the shortcoming of low-temperature industrial handpiece Water Chilling Units is:
(1) sub-load Energy Efficiency Ratio (COP) is low
Unit operation is when sub-load, and Energy Efficiency Ratio (COP) does not only raise, and reduces on the contrary, and decay is serious, and when unit runs under 50% load, Energy Efficiency Ratio (COP) is only during oepration at full load 70%;
(2) unit energy-conditioning range is narrow
The energy-conditioning range of usual unit is 50% ~ 100% or 66% ~ 100%, but and often there is larger fluctuation in the thermic load on production line, if when load fluctuates between 0 ~ 50% or 0 ~ 66%, very easily cause unit frequent start-stop, cause chilled water leaving water temperature fluctuation range large, the needs of user's production technology to temperature cannot be met, have a strong impact on production line production efficiency and Qualified Products Rate; In addition, the frequent start-stop of unit causes great waste of energy, causes the frequent impact to electrical network, has had a strong impact on the life-span of unit, considerably increases the maintaining cost of unit;
(3) maintaining inconvenience
Compressor is mechanical operating part; inevitably there is fault rate; single compressor Cool-water Machine for Industry group is owing to only having a compressor; year long operational time; fault rate is high, and when a failure occurs, a whole set of unit needs maintenance down; corresponding client's production line also will stop production thereupon, cause heavy economic losses.
2. low-temperature industrial handpiece Water Chilling Units in the another kind of multi-compressor used in the market, use more than Liang Tai and two compressor, every compressor carries an independently refrigerating circuit, and namely each refrigerant side loop is completely independent, but shares a set of cooling water channel system and a set of freezing water circuit system.In this system, each independently refrigerating circuit comprises one and carries one-level oil gas divergence type semi-hermetic screw compressor, water-cooled condenser, a dry evaporator, an energy-saving appliance and a secondary oil separator (without oil storage function), and all compressors are controlled by a set of microcomputer control system.In this system, the structural shape of water-cooled condenser has two kinds: 1) each refrigerating circuit configures the water-cooled condenser of a platform independent; 2) ownership cold loop configures a refrigerant side multiloop, cooling water side single loop type water-cooled condenser, is separated between each refrigerant loop by welding blind plate.In this unit, the structural shape of dry evaporator has two kinds: 1) ownership cold loop configures a refrigerant side multiloop, chilled water side single loop type dry evaporator, two parts of barrel lenght half all adopt U heat exchange asymmetrical arrangement, and this structure is only suitable for double-compressor head unit; 2) ownership cold loop configures a refrigerant side multiloop, chilled water side single loop type dry evaporator, and point loop dividing plate by flat head between each refrigerant loop separates.This units' installation is on a steel carrier frame, and outward appearance appears as a set of unit, is actually the simple and mechanical combination of many cover units, is referred to as " false Parallel sets " in industry.In this multi-compressor, the shortcoming of low-temperature industrial handpiece Water Chilling Units is:
(1) heat exchange area utilization rate is low
When unit cuts off a compressor, the corresponding whole refrigerating circuit of this compressor all quits work, and the heat exchange area utilization rate of water-cooled condenser and dry evaporator also decreases.For low-temperature industrial handpiece Water Chilling Units in double-compressor, in the out-of-work situation of a compressor, the utilization rate of water-cooled condenser and dry evaporator heat exchange area only has 50%.For low-temperature industrial handpiece Water Chilling Units in three compressors, in the out-of-work situation of a compressor, the utilization rate of water-cooled condenser and dry evaporator heat exchange area only has 66%, in the out-of-work situation of two compressors, the utilization rate of water-cooled condenser and dry evaporator heat exchange area only has 33%, and the operational energy efficiency ratio (COP) of reduction to unit of heat exchange area utilization rate is totally unfavorable;
(2) gs-oil separator weak effect
When unit cuts off a compressor, the corresponding whole refrigerating circuit of this compressor all quits work (gs-oil separator is no exception), causes oil gas separation at part load to improve;
(3) unit energy-conditioning range is narrow
Single compressor can only operate in the Load Regulation interval of 50% ~ 100% or 66% ~ 100%, and for low-temperature industrial handpiece Water Chilling Units in double-compressor, energy-conditioning range can be widened to 25% ~ 100% or 33% ~ 100%.For low-temperature industrial handpiece Water Chilling Units in three compressors, energy-conditioning range can be widened to 17% ~ 100% or 22% ~ 100%.If when load is between 0 ~ 17% or 0 ~ 22%, unit cannot normally run continuously.
3. in the single compressor existing market used, in low-temperature industrial handpiece Water Chilling Units and multi-compressor, other common drawback of low-temperature industrial handpiece Water Chilling Units is:
(1) Energy Efficiency Ratio (COP) is low at full capacity
Unit adopts water-cooled condenser and dry evaporator, for water-cooled condenser, at least will ensure the heat transfer temperature difference of 12 DEG C ~ 15 DEG C between condensation temperature and air ' s wet bulb temperature, employing be secondary heat exchange system, cause huge energy dissipation.Adopt the easy secondary oil gas separator not with oil storage space, oil gas separation is poor, causes lubricating oil to enter refrigerant system, and forms oil film thermal resistance on heat exchanger tube surface, reduces heat exchange efficiency, adds energy consumption.For dry evaporator, owing to being control liquid supply rate by the degree of superheat, very easily there is excessive dry blowing phenomenon, and after lubricating oil enters dry evaporator heat exchanger tube, very easily form the larger oil film of viscosity at low ambient temperatures, greatly reduce the heat exchange efficiency of dry evaporator, add the energy consumption of unit.Unit compression cooling adopts hydrojet state refrigerant cools, adds the power consumption of unit;
(2) sub-load Energy Efficiency Ratio (COP) is low
<1> is for low-temperature industrial handpiece Water Chilling Units in single compressor, although heat exchange area utilization rate is 100%, but due to the energy adjustment characteristic of helical-lobe compressor itself, unit operation Energy Efficiency Ratio (COP) when sub-load is caused not only not raise, reduce on the contrary, and decay is serious, when unit runs under 50% load, Energy Efficiency Ratio (COP) is only during oepration at full load 70%;
<2> is for low-temperature industrial handpiece Water Chilling Units in multi-compressor, order energy adjustment is carried out owing to adopting multiple compressors, improve the comprehensive energy efficiency ratio (COP) of sub-load, but because unit is when operation at part load, the utilization rate of heat exchange area is very low, and this must cause the decline of unit part Energy Efficiency Ratio (COP);
<3> is when unit is in operation at part load, liquid supply rate reduces thereupon, dry evaporator heat exchanger tube inner refrigerant flow velocity reduces, the coefficient of heat transfer is decayed along with the decline of velocity in pipes, and cause in time the lubricating oil band deposited in heat exchanger tube to be back to compressor because flow velocity reduces, greatly reduce heat exchange efficiency, result in the reduction of sub-load Energy Efficiency Ratio (COP).
(3) energy adjustment of 0 ~ 100% can not be realized
For low-temperature industrial handpiece Water Chilling Units in single compressor, the energy-conditioning range of 50% ~ 100% or 66% ~ 100% can only be realized.For low-temperature industrial handpiece Water Chilling Units in double-compressor, energy-conditioning range can be widened to 25% ~ 100% or 33% ~ 100%.For low-temperature industrial handpiece Water Chilling Units in three compressors, energy-conditioning range can be widened to 17% ~ 100% or 22% ~ 100%;
(4) when starting, lubricating oil oil spout pressure reduction is set up slowly
Screw compressor is oil flooded compressors, in startup and steady running process, all needs the lubricating oil of q.s lubricate running gear and the field of conjugate action and seal.When particularly starting unit in the winter time, because environment temperature is low, cause pressure reduction to be set up more slow, compressor is in oil starvation state for a long time, has a strong impact on the life-span of the running gears such as bearing of compressor, rotor, guiding valve;
(5) in conditioning in Transition Season, winter operation situation, frozen-free hypotony controls
The favourable one side of low condensing pressure is the reduction that can bring unit operation energy consumption, but too low condensing pressure, following problem will be caused: gs-oil separator effect lost efficacy, there is the oily phenomenon of serious race in system, supplying valve pressure reduction reduces to cause feed flow not enough, chilled water temperature cannot cool to and require temperature, and unit occurs that low pressure of inspiration(Pi) is protected;
(6) lubricating oil oil spout temperature is too high
The lubricant effect of oil spout temperature to compressor of lubricating oil is most important, if oil spout temperature is too high, will cause lubrication and seal failure.If temperature is too low, will cause guiding valve lost efficacy and oil strainer pressure reduction excessive, the most suitable oil spout temperature range of helical-lobe compressor is 50 DEG C ~ 60 DEG C.And conventional rack adopts Liquid injection cooling, delivery temperature controls at 85 DEG C ~ 95 DEG C, this means that oil spout temperature is at 85 DEG C ~ 95 DEG C, higher than most suitable oil spout temperature, had a strong impact on the lubricant effect of compressor operation parts, sealing effectiveness is also deteriorated simultaneously, and compression efficiency reduces greatly;
(7) oil return weak effect
Lubricating oil relies on refrigerant flow rates to take back compressor, under low-temperature condition, lubricating oil viscosity is larger, very easily be attached to heat exchanger tube surface, form oil film, at part load, this situation is more serious, not only reduces heat exchange efficiency, if the lubricating oil in refrigeration system cannot get back to compressor all the time in time, the too low protection of compressor oil level will be caused to shut down, cannot normally run, can only repairing to oil level switch reset after, could start shooting, and the lubricating oil in refrigeration system can be cumulative, unit finally also will be caused normally to run;
(8) air entry gas in the middle of compressor, noise are large
The middle suction inlet of compressor, for the gas returning port of energy-saving appliance, due to the fluctuation of operating mode load and the change of Meteorological Elements in China, the pressure of middle suction inlet place compression chamber also fluctuate by the moment, cause the refrigerant gas in muffler to occur just flowing the periodic phenomena with reflux, cause the generation of pulsation and noise;
(9) compressor maintenance difficulty
The compressor adopted is the semi-hermetic screw compressor carrying oil storage space, break down at compressor, when needing field-strip, except the gaseous refrigerant in compressor cavity will being drained, lubricating oil is also needed all to drain, for not exposing the stronger POE lubricating oil of hygroscopicity in an atmosphere for a long time, so when each dismounting compressor, to need lubricating oil by discharge of pipes in vacuum airtight container, compressor is injected with gear pump again after maintenance, or directly change new oil, which results in great waste, and bring difficulty to working after sale.
Summary of the invention
Technical problem to be solved by this invention overcomes the deficiencies in the prior art, provide one can improve simultaneously at full capacity Energy Efficiency Ratio (COP) and sub-load comprehensive energy efficiency ratio (COP), improve unit operation stability, reduce low-temperature cold water unit and operation method thereof in the full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type of unit maintenance cost of upkeep.
Technical scheme of the present invention is as follows:
In full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type involved in the present invention, low-temperature cold water unit comprises the semi-hermetic screw compressor group be made up of semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B), air-breathing screw down nonreturn valve (2A), air-breathing screw down nonreturn valve (2B), exhaust screw down nonreturn valve (3A), exhaust screw down nonreturn valve (3B), magnetic valve (4A), magnetic valve (4B), magnetic valve (5A), magnetic valve (5B), oil return solenoid valve (6A), oil return solenoid valve (6B), solenoid fuel injection valve (7A), solenoid fuel injection valve (7B), oil flow switch (8A), oil flow switch (8B), check-valves (9A), check-valves (9B), gs-oil separator (10), oil level switch (11), lubricating oil temperature sensor (12), electric lubricating oil heater (13), fuel feeding pressure-difference valve (14), pressure sensor (15), evaporative condenser (16), high-pressure reservoir (17), device for drying and filtering (18), refrigerant charging valve (19), bypass cutoff valve (20), bypass cutoff valve (21), humidity indication view mirror (22), thermal siphon oil cooler (23), oil temperature threeway direct-operated regulator (24), energy-saving appliance (25), liquid filter (26A), liquid filter (26B), energy-saving appliance liquid supply electromagnetic valve (27A), energy-saving appliance liquid supply electromagnetic valve (27B), level control control valve (28), fluid level controller (29), main feed flow liquid filter (30), manual throttle valve (31), liquid-level switch (32), frost prevention anti-leak oppositely automatically shuts down plate-type liquid level gauge (33), low pressure recirculating gas liquid/gas separator (34), thermal siphon flooded evaporator (35), ejecting scavenge return device (36), magnetic valve (37), downstream pressure controls direct-operated regulator (38), control system (39) and relevant other manually-operated gate (40), instrument (41) and pipeline (42) etc., the exhaust main road (42a) of described parallel-screw compressor connects the import of oil eliminator (10), the refrigerant outlet of gs-oil separator (10) connects the import of evaporative condenser (16) by pipeline (42b), the lubricating oil outlet of gs-oil separator (10) connects the import of thermal siphon oil cooler (23) lubricating oil by pipeline (42c), thermal siphon oil cooler (23) lubrication oil outlet is by the middle jet of pipeline (42d) connecting screw rod parallel compressor unit, the outlet of evaporative condenser (16) connects the import of high-pressure reservoir (17) by pipeline (42e), the outlet of the main feed flow of high-pressure reservoir (17) system connects by pipeline (42f) import that cold side crossed by energy-saving appliance (25), the thermal siphon oil cooling of high-pressure reservoir (17) but feed flow outlet connects thermal siphon oil cooler (23) refrigerant inlet by pipeline (42g), high-pressure reservoir (17) pressure equalization vent is connected to pipeline (42b) by pipeline (42u), thermal siphon oil cooler (23) refrigerant outlet connects high-pressure reservoir thermal siphon oil cooling but return air inlet by pipeline (42h), the outlet of energy-saving appliance (25) mistake cold side connects the feed flow import of low pressure recirculating gas liquid/gas separator (34) by pipeline (42i), the import of energy-saving appliance (25) throttling side is connected to pipeline (42f) by pipeline (42j), the outlet of energy-saving appliance (25) throttling side is by pipeline (42kA), (42kB) import of the middle air-breathing of difference connecting screw rod parallel compressor unit, the outlet of low pressure recirculating gas liquid/gas separator (34) gaseous refrigerant is by pipeline (42L) connecting screw rod parallel compressor unit air entry, the outlet of low pressure recirculating gas liquid/gas separator (34) liquid refrigerant connects the import of thermal siphon flooded evaporator (35) by pipeline (42m), the outlet of thermal siphon flooded evaporator (35) connects by pipeline (42n) import that low pressure recirculating gas liquid/gas separator (34) refluxes, low pressure recirculating gas liquid/gas separator (35) returns oil outlet connects ejecting scavenge return device (36) sampling fluid import by pipeline (42o), ejecting scavenge return device (36) returns the import of oil outlet by pipeline (42p) connecting screw rod parallel compressor unit air-breathing, ejecting scavenge return device (36) high-pressure hot gas import is connected to pipeline (42b) by pipeline (42q), the bypass line that pipeline (42r) is pipeline (42f), compressor electric motor winding cooling mouth spray is connected to pipeline (42i) by pipeline (42s), downstream pressure controls direct-operated regulator (38) two ends are connected to pipeline (42q) and pipeline (42i) respectively low-pressure end by pipeline (42t), the pressure tappings of fuel feeding pressure-difference valve (14) is connected to pipeline (42L) by pipeline (42v), fuel feeding pressure-difference valve (14) described in the upper installation of pipeline (42b) and pressure sensor (15), lubricating oil pipeline (42c) arranges oil temperature threeway direct-operated regulator (24), solenoid fuel injection valve (7A), solenoid fuel injection valve (7B), oily flow switch (8A), oily flow switch (8B), magnetic valve (4A), magnetic valve (4B) are set on two arms of described pipeline (42d) respectively, three interfaces connecting line (42o), (42p), (42q) respectively of described ejecting scavenge return device (36), described pipeline (42q) is installed magnetic valve (37), two arms of described pipeline (42p) are installed respectively magnetic valve (6A) and magnetic valve (6B), described pipeline (42f) is arranged coolant injection bypass line (42r), described bypass line (42r) is arranged device for drying and filtering (18), refrigerant charging valve (19), bypass cutoff valve (20), bypass cutoff valve (21) and humidity indication view mirror (22), described pipeline (42t) is arranged downstream pressure and control direct-operated regulator (38), described magnetic valve (27A), magnetic valve (27B) are front arranges liquid filter (26A) and liquid filter (26B) respectively, lubricating oil temperature sensor (12) and electric lubricating oil heater (13) are installed in described gs-oil separator (10) bottom, the main feed flow liquid filter (30) of the front installation of described level control control valve (28), described gas-liquid separator (34) is installed liquid-level switch (32) and frost prevention anti-leak oppositely automatically shuts down plate-type liquid level gauge (33), the middle air entry pipeline (42kA) of described semi-hermetic screw compressor (1A), semi-hermetic screw compressor (1B) and (42kB) arrange check-valves (9A) and check-valves (9B) respectively.
Compared with prior art, beneficial effect of the present invention is as follows:
(1) compared to low-temperature industrial handpiece Water Chilling Units in low-temperature industrial handpiece Water Chilling Units in traditional single compressor and multi-compressor, Energy Efficiency Ratio (COP) improves more than 30% at full capacity, and sub-load comprehensive energy efficiency ratio (COP) improves more than 50%;
(2) compared to low-temperature industrial handpiece Water Chilling Units in low-temperature industrial handpiece Water Chilling Units in traditional single compressor and multi-compressor, the energy-conditioning range of 0 ~ 100% can be realized;
(3) compared to low-temperature industrial handpiece Water Chilling Units in low-temperature industrial handpiece Water Chilling Units in traditional single compressor and multi-compressor, chilled water leaving water temperature can realize ± control accuracy of 0.5 DEG C;
Compared to low-temperature industrial handpiece Water Chilling Units in low-temperature industrial handpiece Water Chilling Units in traditional single compressor and multi-compressor, maintaining cost reduces by more than 50%, and unit operation is safer, reliable, stable.
Accompanying drawing explanation
Fig. 1 is the circulatory system schematic diagram of low-temperature cold water unit in full working scope high-efficiency evaporating of the present invention cold screw parallel thermal siphon full-liquid type.
Detailed description of the invention
Below in conjunction with the drawings and specific embodiments, using method of the present invention is further described.
Please first consult Fig. 1, Fig. 1 is the circulatory system schematic diagram of low-temperature cold water unit in full working scope high-efficiency evaporating of the present invention cold screw parallel thermal siphon full-liquid type.
In described full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type, the using method of low-temperature cold water unit divides the following steps:
(1) unit first refrigerant charging operation: unit first charging refrigerant time, in order to ensure that the moisture of the cold-producing medium be filled with in system is within allowed band, bypass cutoff valve (20) is closed when filling, open bypass cutoff valve (21) and refrigerant charging valve (19), allow filled cold-producing medium first enter system pipeline and high-pressure reservoir (17) through device for drying and filtering (18) and humidity indication view mirror (22); After filling, close refrigerant charging valve (19) and open bypass cutoff valve (20), now bypass line (42r) not only can play the effect that sampling detects, and also determines whether to need to change the dry filter core in device for drying and filtering (18) by the upper humidity indication view mirror (22) installed of bypass line (42r); When changing the dry filter core in device for drying and filtering (18), close bypass cutoff valve (20) and bypass cutoff valve (21), now unit still can normally run simultaneously;
(2) the unit starting preparatory stage: connect main power source and control system (39) power supply, check in control system (39) touch screen with or without fault alarm information, check whether chilled water pump and evaporative condenser (16) normally start, check whether the oil temperature that lubricating oil temperature sensor (12) is measured has reached permission start-up temperature;
(3) the unit starting stage: first start helical-lobe compressor (1A) or helical-lobe compressor (1B), if first start helical-lobe compressor (1A), solenoid fuel injection valve (7A) opened by interlocking simultaneously, energy-saving appliance liquid supply electromagnetic valve (27A) and level control control valve (28), compressor 25% completes smoothly startup stage after, enter the normal operation stage, whether normally start to detect parameters, and according to chilled water leaving water temperature, determine to continue to load still to rest on 25% continuous service, the total run time can accumulated according to control system (39) internal processes and the time relay between each compressor, after unit shuts down a period of time according to chilled water leaving water temperature automatic cycle due to water temperature rise need again the prerequisite again started under, automatic selection switchover operation,
(4) control logic of electric lubricating oil heater (13): if unit is in lubricating oil temperature in stopped status and gs-oil separator (10) lower than 50 DEG C, electric lubricating oil heater (13) is started working; If unit is in operating condition, no matter the height of gs-oil separator (10) interior lubricating oil temperature, electric lubricating oil heater (13) is all in off working state;
(5) adjustment of fuel feeding pressure-difference valve (14): unit is in start-up course, require built-inly to base oneself upon enough fuel feeding pressure reduction in the regular hour, to ensure that the oil starvation time of compressor can not be long, the valve body of fuel feeding pressure-difference valve (14) has two pressure tappings, one is pressure at expulsion pressure tappings, and another is pressure of inspiration(Pi) pressure tappings, when pressure reduction is less than required minimum fuel feeding pressure reduction, valve starts to turn down, and reduce if continue, valve turns down always until full cut-off; When pressure reduction is higher than required minimum fuel feeding pressure reduction, valve starts out greatly, raises if continue, and valve one heads straight for large until standard-sized sheet;
(6) unit condensation pressure regulation: in unit normal course of operation, pressure sensor (15) is according to measuring the real-time condensing pressure of unit, the cooling fan rotation speed of VFC evaporative condenser (16) and the start and stop of feeding spraying pump, when unit condensing pressure is lower than a certain value, the cooling fan rotation speed of evaporative condenser (16) reduces; If when cooling fan has reached low-limit frequency, when condensing pressure is also at continuous decrease until lower than another value, close the feeding spraying pump of evaporative condenser (16), in condensing pressure control procedure, also need to consider certain moment scope, avoid equipment frequent start-stop;
(7) unit delivery temperature and motor winding temperature control: unit is in running, the exhaust high temperature protection PTC sensor that these two temperature values are respectively carried by semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B) and motor winding temperature protection PTC sensor are measured in real time, if when semi-hermetic screw compressor (1A) delivery temperature reaches temperature too high setting value, then open magnetic valve (5A); If when semi-hermetic screw compressor (1B) delivery temperature reaches temperature too high setting value, then open magnetic valve (5B); If when semi-hermetic screw compressor (1A) motor winding temperature reaches temperature too high setting value, then open magnetic valve (4A); If when semi-hermetic screw compressor (1B) motor winding temperature reaches temperature too high setting value, then open magnetic valve (4B);
(8) unit oil return system control logic: at semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B) all when running, when lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6A), oil return solenoid valve (6B), magnetic valve (37); When only having semi-hermetic screw compressor (1A) to run, when the lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6A), magnetic valve (37); When only having semi-hermetic screw compressor (1B) to run, when the lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6B), magnetic valve (37); Described ejecting scavenge return device (13) is opened periodically and batch (-type) oil return pattern according to the setting of control system (39) the interior time relay;
(9) adjustment of unit oil temperature supplying: oil temperature threeway direct-operated regulator (24) has three interfaces, is respectively hot oil inlet, cold oil import and warm oil export, no matter under any circumstance, can ensure that the oil temperature supplying of unit is stabilized in optimum temperature;
(10) unit Liquid level and protection: utilize the liquid refrigerant liquid level that the cooperation of level control control valve (28) and fluid level controller (29) accurately controls in low pressure recirculating gas liquid/gas separator (34); Fluid level controller (29) is by transmission of pressure signal to level control control valve (28), and the feed flow realizing 0 ~ 100% regulates; Solenoid pilot valve on level control control valve (28) and operating states of the units interlocking, open and close main liquid feeding pipeline; If unit occurs the too high situation of liquid level in running mesolow recirculating gas liquid/gas separator (34), in order to prevent compressor from may damage because of absorbing gas belt liquid, cut off unit operation by liquid-level switch (32) action;
(11) feed flow bypass line operation: when the filter screen in main feed flow liquid filter (30) needs cleaning or level control control valve (28) and fluid level controller (29) to break down, open manual throttle valve (31) to correct position, and close the cut-off service valve on main liquid feeding pipeline both sides, now unit still can normally run.
Claims (4)
1. the present invention relates to low-temperature cold water unit in a kind of full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type of industrial refrigeration field, it comprises the semi-hermetic screw compressor group be made up of semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B) and (only describes structure and the method for operation of this system in these claims for two semi-hermetic screw compressors, but involved in the present invention to the number of compressors of this compressor bank be not limited to 2, therefore, every on this invention basis to compressor bank in the scheme that increases and decreases of number of compressors all within scope), air-breathing screw down nonreturn valve (2A), air-breathing screw down nonreturn valve (2B), exhaust screw down nonreturn valve (3A), exhaust screw down nonreturn valve (3B), magnetic valve (4A), magnetic valve (4B), magnetic valve (5A), magnetic valve (5B), oil return solenoid valve (6A), oil return solenoid valve (6B), solenoid fuel injection valve (7A), solenoid fuel injection valve (7B), oil flow switch (8A), oil flow switch (8B), check-valves (9A), check-valves (9B), gs-oil separator (10), oil level switch (11), lubricating oil temperature sensor (12), electric lubricating oil heater (13), fuel feeding pressure-difference valve (14), pressure sensor (15), evaporative condenser (16), high-pressure reservoir (17), device for drying and filtering (18), refrigerant charging valve (19), bypass cutoff valve (20), bypass cutoff valve (21), humidity indication view mirror (22), thermal siphon oil cooler (23), oil temperature threeway direct-operated regulator (24), energy-saving appliance (25), liquid filter (26A), liquid filter (26B), energy-saving appliance liquid supply electromagnetic valve (27A), energy-saving appliance liquid supply electromagnetic valve (27B), level control control valve (28), fluid level controller (29), main feed flow liquid filter (30), manual throttle valve (31), liquid-level switch (32), frost prevention anti-leak oppositely automatically shuts down plate-type liquid level gauge (33), low pressure recirculating gas liquid/gas separator (34), thermal siphon flooded evaporator (35), ejecting scavenge return device (36), magnetic valve (37), downstream pressure controls direct-operated regulator (38), electric control box (39) and relevant other manually-operated gate (40), instrument (41) and pipeline (42) etc., the exhaust main road (42a) of described parallel-screw compressor connects the import of gs-oil separator (10), the refrigerant outlet of gs-oil separator (10) connects the import of evaporative condenser (16) by pipeline (42b), the lubricating oil outlet of gs-oil separator (10) connects the import of thermal siphon oil cooler (23) lubricating oil by pipeline (42c), thermal siphon oil cooler (23) lubrication oil outlet is by the middle jet of pipeline (42d) connecting screw rod parallel compressor unit, the outlet of evaporative condenser (16) connects the import of high-pressure reservoir (17) by pipeline (42e), the outlet of the main feed flow of high-pressure reservoir (17) system connects by pipeline (42f) import that cold side crossed by energy-saving appliance (25), the thermal siphon oil cooling of high-pressure reservoir (17) but feed flow outlet connects thermal siphon oil cooler (23) refrigerant inlet by pipeline (42g), high-pressure reservoir (17) pressure equalization vent is connected to pipeline (42b) by pipeline (42u), thermal siphon oil cooler (23) refrigerant outlet connects high-pressure reservoir thermal siphon oil cooling but return air inlet by pipeline (42h), the outlet of energy-saving appliance (25) mistake cold side connects the feed flow import of low pressure recirculating gas liquid/gas separator (34) by pipeline (42i), the import of energy-saving appliance (25) throttling side is connected to pipeline (42f) by pipeline (42j), the outlet of energy-saving appliance (25) throttling side is by pipeline (42kA), (42kB) import of the middle air-breathing of difference connecting screw rod parallel compressor unit, the outlet of low pressure recirculating gas liquid/gas separator (34) gaseous refrigerant is by pipeline (42L) connecting screw rod parallel compressor unit air entry, the outlet of low pressure recirculating gas liquid/gas separator (34) liquid refrigerant connects the import of thermal siphon flooded evaporator (35) by pipeline (42m), the outlet of thermal siphon flooded evaporator (35) connects by pipeline (42n) import that low pressure recirculating gas liquid/gas separator (34) refluxes, low pressure recirculating gas liquid/gas separator (35) returns oil outlet connects ejecting scavenge return device (36) sampling fluid import by pipeline (42o), ejecting scavenge return device (36) returns the import of oil outlet by pipeline (42p) connecting screw rod parallel compressor unit air-breathing, ejecting scavenge return device (36) high-pressure hot gas import is connected to pipeline (42b) by pipeline (42q), the bypass line that pipeline (42r) is pipeline (42f), compressor electric motor winding cooling mouth spray is connected to pipeline (42i) by pipeline (42s), downstream pressure controls direct-operated regulator (38) two ends are connected to pipeline (42q) and pipeline (42i) respectively low-pressure end by pipeline (42t), the pressure tappings of fuel feeding pressure-difference valve (14) is connected to pipeline (42L) by pipeline (42v).
2. in full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type as claimed in claim 1, the feature of low-temperature cold water unit is: described high-pressure reservoir (17) is except the reservoir as main liquid-supplying system, simultaneously as the thermal siphon recirculation storage tank of thermal siphon oil cooler (23), described pipeline (42g) stretches into high-pressure reservoir (17) structure in being.
3. in full working scope high-efficiency evaporating cold screw parallel thermal siphon full-liquid type as claimed in claim 1, the feature of low-temperature cold water unit is also: the fuel feeding pressure-difference valve (14) described in the upper installation of pipeline (42b) and pressure sensor (15); Lubricating oil pipeline (42c) arranges oil temperature threeway direct-operated regulator (24); Solenoid fuel injection valve (7A), solenoid fuel injection valve (7B), oily flow switch (8A), oily flow switch (8B), magnetic valve (4A), magnetic valve (4B) are set on two arms of described pipeline (42d) respectively; Three interfaces connecting line (42o), (42p), (42q) respectively of described ejecting scavenge return device (36), described pipeline (42q) is installed magnetic valve (37), two arms of described pipeline (42p) are installed respectively magnetic valve (6A) and magnetic valve (6B); Described pipeline (42f) is arranged coolant injection bypass line (42r), described bypass line (42r) is arranged device for drying and filtering (18), refrigerant charging valve (19), bypass cutoff valve (20), bypass cutoff valve (21) and humidity indication view mirror (22); Described pipeline (42t) is arranged downstream pressure and control direct-operated regulator (38); Described magnetic valve (27A), magnetic valve (27B) are front arranges liquid filter (26A) and liquid filter (26B) respectively; Lubricating oil temperature sensor (12) and electric lubricating oil heater (13) are installed in described gs-oil separator (10) bottom; The main feed flow liquid filter (30) of the front installation of described level control control valve (28); Described gas-liquid separator (34) is installed liquid-level switch (32) and frost prevention anti-leak oppositely automatically shuts down plate-type liquid level gauge (33); The middle air entry pipeline of described semi-hermetic screw compressor (1A), semi-hermetic screw compressor (1B) is arranged respectively check-valves (9A) and check-valves (9B).
4. in full working scope high-efficiency evaporating according to claim 1 cold screw parallel thermal siphon full-liquid type, the feature of the operation method of low-temperature cold water unit is to consist of the following components:
(1) unit first refrigerant charging operation: unit first charging refrigerant time, in order to ensure that the moisture of the cold-producing medium be filled with in system is within allowed band, bypass cutoff valve (20) is closed when filling, open bypass cutoff valve (21) and refrigerant charging valve (19), allow filled cold-producing medium first enter system pipeline and high-pressure reservoir (17) through device for drying and filtering (18) and humidity indication view mirror (22); After filling, close refrigerant charging valve (19) and open bypass cutoff valve (20), now bypass line (42r) not only can play the effect of sampling on-line checkingi, also determines whether to need to change the dry filter core in device for drying and filtering (18) by the upper humidity indication view mirror (22) installed of bypass line (42r); When changing the dry filter core in device for drying and filtering (18), close bypass cutoff valve (20) and bypass cutoff valve (21), now unit still can normally run simultaneously;
(2) the unit starting preparatory stage: connect main power source and control system (39) power supply, check in control system (39) touch screen with or without fault alarm information, check whether chilled water pump and evaporative condenser (16) normally start, check whether the oil temperature that lubricating oil temperature sensor (12) is measured reaches permission start oil temperature (hereafter for 50 DEG C);
(3) the unit starting stage: first start helical-lobe compressor (1A) or helical-lobe compressor (1B), if first start helical-lobe compressor (1A), solenoid fuel injection valve (7A) opened by interlocking simultaneously, energy-saving appliance liquid supply electromagnetic valve (27A) and level control control valve (28), compressor 25% completes smoothly startup stage after, enter the normal operation stage, whether normally start to detect parameters, and according to chilled water leaving water temperature, determine to continue to load still to rest on 25% continuous service, the total run time can accumulated according to control system (39) internal processes and the time relay between each compressor, after unit shuts down a period of time according to chilled water leaving water temperature automatic cycle due to water temperature rise need again the prerequisite again started under, automatic selection switchover operation,
(4) control logic of electric lubricating oil heater (13): if unit is in lubricating oil temperature in stopped status and gs-oil separator (10) lower than 50 DEG C, electric lubricating oil heater (13) is started working; If unit is in operating condition, no matter the lubricating oil temperature in gs-oil separator (10) is how many, electric lubricating oil heater (13) is all in off working state;
(5) adjustment of fuel feeding pressure-difference valve (14): unit is in start-up course, require built-inly to base oneself upon enough fuel feeding pressure reduction in the regular hour, to ensure that the oil starvation time of compressor can not be long, the valve body of fuel feeding pressure-difference valve (14) has two pressure tappings, one is pressure at expulsion pressure tappings, and another is pressure of inspiration(Pi) pressure tappings, when pressure reduction is less than required minimum fuel feeding pressure reduction, valve starts to turn down, and reduce if continue, valve turns down always until full cut-off; When pressure reduction is higher than required minimum fuel feeding pressure reduction, valve starts out greatly, raises if continue, and valve one heads straight for large until standard-sized sheet;
(6) unit condensation pressure regulation: in unit normal course of operation, pressure sensor (15) is according to measuring the real-time condensing pressure of unit, the cooling fan rotation speed of VFC evaporative condenser (16) and the start and stop of feeding spraying pump, when unit condensing pressure is lower than a certain value, the cooling fan rotation speed of evaporative condenser (16) reduces; If when cooling fan has reached low-limit frequency, when condensing pressure is also at continuous decrease until lower than another value, close the feeding spraying pump of evaporative condenser (16), in condensing pressure control procedure, also need to consider certain moment scope, avoid equipment frequent start-stop;
(7) unit delivery temperature and motor winding temperature control: unit is in running, the exhaust high temperature protection PTC sensor that these two temperature values are respectively carried by semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B) and motor winding temperature protection PTC sensor are measured in real time, if when semi-hermetic screw compressor (1A) delivery temperature reaches temperature too high setting value, then open magnetic valve (5A); If when semi-hermetic screw compressor (1B) delivery temperature reaches temperature too high setting value, then open magnetic valve (5B); If when semi-hermetic screw compressor (1A) motor winding temperature reaches temperature too high setting value, then open magnetic valve (4A); If when semi-hermetic screw compressor (1B) motor winding temperature reaches temperature too high setting value, then open magnetic valve (4B);
(8) unit oil return system control logic: at semi-hermetic screw compressor (1A) and semi-hermetic screw compressor (1B) all when running, when lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6A), oil return solenoid valve (6B), magnetic valve (37); When only having semi-hermetic screw compressor (1A) to run, when the lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6A), magnetic valve (37); When only having semi-hermetic screw compressor (1B) to run, when the lubricating oil level in gs-oil separator (10) is reduced to protection oil level, oil level switch (11) action, touches simultaneously and opens oil return solenoid valve (6B), magnetic valve (37); Described ejecting scavenge return device (13) is opened periodically and batch (-type) oil return pattern according to the setting of control system (39) the interior time relay;
(9) adjustment of unit oil temperature supplying: oil temperature threeway direct-operated regulator (24) has three interfaces, is respectively hot oil inlet, cold oil import and warm oil export, no matter under any circumstance, can ensure that the oil temperature supplying of unit is stabilized in optimum temperature;
(10) unit Liquid level and protection: utilize the liquid refrigerant liquid level that the cooperation of level control control valve (28) and fluid level controller (29) accurately controls in low pressure recirculating gas liquid/gas separator (34); Fluid level controller (29) is by transmission of pressure signal to level control control valve (28), and the feed flow realizing 0 ~ 100% regulates; Solenoid pilot valve on level control control valve (28) and operating states of the units interlocking, open and close main liquid feeding pipeline; If unit occurs the too high situation of liquid level in running mesolow recirculating gas liquid/gas separator (34), in order to prevent compressor from may damage because of absorbing gas belt liquid, cut off unit operation by liquid-level switch (32) action;
(11) feed flow bypass line operation: when the filter screen in main feed flow liquid filter (30) needs cleaning or level control control valve (28) and fluid level controller (29) to break down, open manual throttle valve (31) to correct position, and close the cut-off service valve on main liquid feeding pipeline both sides, now unit still can normally run.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510669129.6A CN105180491A (en) | 2015-10-18 | 2015-10-18 | Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510669129.6A CN105180491A (en) | 2015-10-18 | 2015-10-18 | Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105180491A true CN105180491A (en) | 2015-12-23 |
Family
ID=54902758
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510669129.6A Pending CN105180491A (en) | 2015-10-18 | 2015-10-18 | Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105180491A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105674611A (en) * | 2016-03-30 | 2016-06-15 | 江西浩金欧博空调制造有限公司 | Siphonic water-cooled screw low-temperature solution unit |
| CN107166790A (en) * | 2017-07-13 | 2017-09-15 | 成都美森制冷设备有限公司 | Hydrocone type water cooling Brine machine groups system |
| CN107394966A (en) * | 2017-07-13 | 2017-11-24 | 中国汽车技术研究中心 | Exhaust device and motor oil cooling device |
| CN107504704A (en) * | 2017-09-18 | 2017-12-22 | 石家庄久鼎制冷空调设备有限公司 | Efficient parallel-screw chilled water system |
| CN108131854A (en) * | 2018-02-09 | 2018-06-08 | 安徽美乐柯制冷空调设备有限公司 | A kind of multi-parallel screw low-temperature handpiece Water Chilling Units of direct-expansion type feed flow |
| CN108150423A (en) * | 2018-01-11 | 2018-06-12 | 无锡锡压压缩机有限公司 | A kind of automatic water replenishing system for screw air compressor of spraying water |
| CN108224858A (en) * | 2018-02-01 | 2018-06-29 | 青岛绿环工业设备有限公司 | A kind of refrigerant recovery system |
| CN109654761A (en) * | 2019-01-31 | 2019-04-19 | 山东欧菲特能源科技有限公司 | A kind of ultralow temperature Frequency Conversion Variable Water Flow low temperature screw rod vortex unit, system and method |
| CN110388775A (en) * | 2019-07-25 | 2019-10-29 | 重庆美的通用制冷设备有限公司 | Water cooler and its control method and device |
| CN112554934A (en) * | 2020-06-05 | 2021-03-26 | 中铁工程装备集团有限公司 | High-efficient ventilation refrigerating system in tunnel |
| CN113404449A (en) * | 2021-06-07 | 2021-09-17 | 丹东市智林测控技术研究所 | Anti-freezing method for rotary steering down-transmission code sending pipeline |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338505A (en) * | 2011-09-30 | 2012-02-01 | Tcl空调器（武汉）有限公司 | Oil return flow path for multi-connected compressors and control method of oil return flow path |
| CN102901259A (en) * | 2012-10-31 | 2013-01-30 | 南京五洲制冷集团有限公司 | Double-machine double-stage compression refrigeration unit |
| CN103162460A (en) * | 2011-12-15 | 2013-06-19 | 同方人工环境有限公司 | Hydraulic filling type screw water-cooled cold water and heat pump unit |
-
2015
- 2015-10-18 CN CN201510669129.6A patent/CN105180491A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338505A (en) * | 2011-09-30 | 2012-02-01 | Tcl空调器（武汉）有限公司 | Oil return flow path for multi-connected compressors and control method of oil return flow path |
| CN103162460A (en) * | 2011-12-15 | 2013-06-19 | 同方人工环境有限公司 | Hydraulic filling type screw water-cooled cold water and heat pump unit |
| CN102901259A (en) * | 2012-10-31 | 2013-01-30 | 南京五洲制冷集团有限公司 | Double-machine double-stage compression refrigeration unit |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105674611A (en) * | 2016-03-30 | 2016-06-15 | 江西浩金欧博空调制造有限公司 | Siphonic water-cooled screw low-temperature solution unit |
| CN107166790A (en) * | 2017-07-13 | 2017-09-15 | 成都美森制冷设备有限公司 | Hydrocone type water cooling Brine machine groups system |
| CN107394966A (en) * | 2017-07-13 | 2017-11-24 | 中国汽车技术研究中心 | Exhaust device and motor oil cooling device |
| CN107394966B (en) * | 2017-07-13 | 2024-01-30 | 中国汽车技术研究中心 | Exhaust apparatus and motor oil cooling device |
| CN107504704A (en) * | 2017-09-18 | 2017-12-22 | 石家庄久鼎制冷空调设备有限公司 | Efficient parallel-screw chilled water system |
| CN108150423A (en) * | 2018-01-11 | 2018-06-12 | 无锡锡压压缩机有限公司 | A kind of automatic water replenishing system for screw air compressor of spraying water |
| CN108224858A (en) * | 2018-02-01 | 2018-06-29 | 青岛绿环工业设备有限公司 | A kind of refrigerant recovery system |
| CN108131854B (en) * | 2018-02-09 | 2023-10-10 | 安徽美乐柯制冷空调设备有限公司 | Direct expansion type liquid supply multi-parallel screw low-temperature water chilling unit |
| CN108131854A (en) * | 2018-02-09 | 2018-06-08 | 安徽美乐柯制冷空调设备有限公司 | A kind of multi-parallel screw low-temperature handpiece Water Chilling Units of direct-expansion type feed flow |
| CN109654761A (en) * | 2019-01-31 | 2019-04-19 | 山东欧菲特能源科技有限公司 | A kind of ultralow temperature Frequency Conversion Variable Water Flow low temperature screw rod vortex unit, system and method |
| CN110388775A (en) * | 2019-07-25 | 2019-10-29 | 重庆美的通用制冷设备有限公司 | Water cooler and its control method and device |
| CN112554934A (en) * | 2020-06-05 | 2021-03-26 | 中铁工程装备集团有限公司 | High-efficient ventilation refrigerating system in tunnel |
| CN113404449A (en) * | 2021-06-07 | 2021-09-17 | 丹东市智林测控技术研究所 | Anti-freezing method for rotary steering down-transmission code sending pipeline |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105180491A (en) | Full-condition efficient evaporation cooled screw parallel-connection thermo-syphon flooded type low-medium temperature water chilling unit | |
| CN102997510B (en) | Apply the Condensing units of evaporative condenser, handpiece Water Chilling Units and refrigeration air-conditioning unit and its control method | |
| CN204460550U (en) | A kind of environment-friendly and energy-efficient humiture control equipment in parallel | |
| CN106642778A (en) | Oilless water chilling unit and air conditioning system | |
| CN104457002B (en) | Integrated double-cooling water chilling unit | |
| CN206670134U (en) | Double low-temperature receiver plate-sheet-type evaporative condenser all-in-ones | |
| US10267548B2 (en) | Oil management for heating ventilation and air conditioning system | |
| CN111947336B (en) | Refrigeration cycle system and control method thereof | |
| CN106152840B (en) | Heat pipe system, refrigeration system and control method thereof | |
| CN104864621B (en) | A kind of four-pipe system Dual-evaporator refrigeration system | |
| CN103344016A (en) | Energy-saving air conditioner for machine room | |
| CN102445036A (en) | Ice making machine | |
| CN109028629A (en) | A kind of carbon dioxide refrigerating medium refrigeration system and its refrigerating method | |
| CN206019098U (en) | Heat of compressor recovery type hot water defrosting's refrigeration system | |
| CN208832629U (en) | A kind of low-temperature cold water unit | |
| CN105910337B (en) | Heat pump | |
| CN208431976U (en) | A kind of carbon dioxide refrigerating medium refrigeration system | |
| CN205192005U (en) | A refrigerating system and freezer that be used for refrigerating system reservoir subassembly, have it | |
| CN209484762U (en) | A kind of double cold source heat pipe air conditioner devices | |
| CN207146962U (en) | A kind of refrigeration system with two-way condenser | |
| CN106066101A (en) | A kind of double-effect heat pump unit | |
| CN206113391U (en) | Cold chain heat recovery refrigerating system | |
| CN209181302U (en) | A kind of sled block formula salt water water cooler | |
| CN206890982U (en) | Cooling and defrost automatic constant temperature system | |
| CN204388410U (en) | The two cold handpiece Water Chilling Units of integral type |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20151223 |