WO2020108005A1 - 一种压缩机、空气调节系统 - Google Patents

一种压缩机、空气调节系统 Download PDF

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Publication number
WO2020108005A1
WO2020108005A1 PCT/CN2019/105336 CN2019105336W WO2020108005A1 WO 2020108005 A1 WO2020108005 A1 WO 2020108005A1 CN 2019105336 W CN2019105336 W CN 2019105336W WO 2020108005 A1 WO2020108005 A1 WO 2020108005A1
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Prior art keywords
compressor
temperature
refrigerant
pipe
heat exchanger
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PCT/CN2019/105336
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English (en)
French (fr)
Inventor
武传志
张捷
隋杰磊
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青岛海尔空调电子有限公司
海尔智家股份有限公司
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Publication of WO2020108005A1 publication Critical patent/WO2020108005A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control

Definitions

  • the invention relates to the technical field of compressors, in particular to a compressor and an air conditioning system.
  • the compressor In the vapor compression refrigeration unit, the compressor is the heart of the refrigeration system.
  • the operating range of the refrigeration unit directly depends on the operating range of the compressor and is limited by the use limit of the compressor, so the lower evaporation temperature cannot be obtained in the evaporator. , In order to prevent the compressor from sucking too low temperature refrigerant to cause damage to the compressor.
  • an intermediate air supplement refrigeration cycle method is to generate a supplement air port in the process of compressing the working fluid of the screw compressor, so that a part of the condensed refrigerant liquid passes through the throttle valve to reduce pressure and is generated after heat exchange in the economizer.
  • the refrigerant vapor enters the compressor through the air supply port and continues to be compressed, which is equivalent to two compressions.
  • supplementing air in the middle of the compressor although it can improve the energy efficiency of the compressor, it still cannot solve the actual operating temperature range. problem.
  • the embodiments of the present invention provide a compressor and an air conditioning system to expand the application scope of the compressor.
  • a brief summary is given below. This summary section is not a general comment, nor is it to determine key/important elements or to describe the scope of protection of these embodiments. Its sole purpose is to present some concepts in a simple form as a preface to the detailed description that follows.
  • a compressor is provided.
  • the compressor includes a compressor body, and further includes a temperature adjustment device for adjusting the suction temperature of the compressor;
  • the temperature adjustment device includes a throttling module and a heat exchanger; the first liquid inlet port of the throttling module is connected to the refrigerant through a first pipe, and the first gas outlet port is connected to the first part of the heat exchanger through a second pipe Two inlet ports, the second outlet port of the heat exchanger is connected to the inlet port of the compressor through a third pipe.
  • a first one-way valve is provided on the third pipe; the first one-way valve controls refrigerant to flow from the second air outlet of the heat exchanger to the compressor for suction mouth.
  • an air conditioning system is provided.
  • the air-conditioning system includes the above-mentioned compressor, and the compressor is connected to the condenser, the throttle valve, and the evaporator in sequence to form a circulation path; the circulation of refrigeration Agent; the first pipe of the temperature adjusting device is connected to the pipe between the condenser and the throttle valve, or the first pipe of the temperature adjusting device is connected to the refrigerant input pipe.
  • a control device for controlling the temperature adjustment device is also included.
  • control device includes: a first unit for controlling the opening of the throttle module; and a second unit for controlling the turning on and off of the temperature adjusting device.
  • a compressor and an air conditioning system provided by the present invention are provided with a temperature regulating device at the suction port of the compressor.
  • the air conditioning system When the air conditioning system is cooled, the refrigerant is connected to the refrigerant through the throttling module connection pipeline, and the heat is exchanged
  • the gas output from the evaporator is mixed into the suction port of the compressor, and the application range of the original compressor is expanded to effectively solve the problem of use beyond the compressor.
  • Fig. 1 is a schematic structural diagram of a compressor according to an exemplary embodiment
  • Fig. 2 is a schematic structural diagram of an air conditioning system according to an exemplary embodiment
  • Fig. 3 is a schematic structural diagram of an air conditioning system according to an exemplary embodiment
  • Fig. 4 is a schematic diagram of connection of a control device of an air conditioning system according to an exemplary embodiment
  • Fig. 5 is a pressure enthalpy diagram of an air conditioning system according to an exemplary embodiment
  • 1-compressor 11-throttling module, 12-heat exchanger, 13-first check valve, 2-condenser, 3-throttle valve, 4-evaporator, 5-second check valve , 6-control device, 61-first unit, 62-second unit.
  • the terms "include”, “include” or any other variant thereof are intended to cover non-exclusive inclusion, so that a structure, device, or device that includes a series of elements includes not only those elements, but also others that are not explicitly listed Elements, or include elements inherent to such structures, devices, or equipment. Without further restrictions, the element defined by the sentence "including one" does not exclude that there are other identical elements in the structure, device or equipment that includes the element.
  • the embodiments in this document are described in a progressive manner. Each embodiment focuses on the differences from other embodiments. The same or similar parts between the embodiments can be referred to each other.
  • connection should be understood in a broad sense, for example, it can be a mechanical connection or an electrical connection, or it can be the communication between two elements, It may be directly connected or indirectly connected through an intermediate medium.
  • connection should be understood in a broad sense, for example, it can be a mechanical connection or an electrical connection, or it can be the communication between two elements, It may be directly connected or indirectly connected through an intermediate medium.
  • connection should be understood in a broad sense, for example, it can be a mechanical connection or an electrical connection, or it can be the communication between two elements, It may be directly connected or indirectly connected through an intermediate medium.
  • the term “plurality” means two or more.
  • A/B means: A or B.
  • a and/or B means: A or B, or A and B.
  • Fig. 1 is a schematic structural diagram of a compressor 1 according to an exemplary embodiment.
  • this embodiment provides a compressor including a compressor body and a temperature adjustment device for adjusting the suction temperature of the compressor; in this embodiment, the refrigerant is temperature-adjusted by the temperature adjustment device After that, it is mixed with the gas normally entering the suction port of the compressor 1 to increase the suction temperature of the compressor 1.
  • the temperature adjustment device includes a throttling module 11 and a heat exchanger 12; the first liquid inlet port of the throttling module 11 is connected to the refrigerant through a first pipe, and the first gas outlet port is connected to the exchange through a second pipe The second inlet port of the heat exchanger 12 and the second outlet port of the heat exchanger 12 are connected to the inlet port of the compressor 1 through a third pipe.
  • the throttling module 11 is used for throttling and depressurizing the incoming refrigerant; the heat exchanger 12 is used to evaporate the incoming refrigerant liquid into superheated steam to raise the suction temperature of the compressor 1.
  • the throttling module 11 includes an electronic expansion valve or an electronic throttle valve, which is used to throttle the pressure and adjust the flow rate.
  • a first one-way valve 13 is provided on the third pipe; the first one-way valve 13 controls the refrigerant to flow from the second outlet port of the heat exchanger 12 to the suction port of the compressor 1. In this way, the refrigerant is prevented from flowing in the reverse direction, affecting the normal operation of the compressor 1.
  • a temperature regulating device is added after the suction port of the compressor 1, the refrigerant is throttled and pressure-regulated, and after being evaporated and heated by the heat exchanger 12, it is mixed with other gases.
  • the scope of application of the compressor is expanded.
  • the throttling module 11 of the temperature regulating device is connected to the refrigerant through the first pipe, and the refrigerant may be a refrigerant liquid discharged from the condenser, after throttling and depressurization by the throttling module 11 It enters the heat exchanger 12 to become superheated steam, or it can be refrigerant or gas connected from any other pipeline, enter the heat exchanger 12 for heat exchange and temperature adjustment, and then pass to the suction port of the compressor 1 to expand air conditioning The scope of use of the original compressor 1 of the system.
  • Fig. 2 is a schematic structural diagram of an air conditioning system according to an exemplary embodiment.
  • this embodiment provides an air conditioning system, including the above-mentioned compressor 1, the compressor 1 is connected to a condenser 2, a throttle valve 3, and an evaporator 4 in sequence to form a circulation path; the pipe Refrigerant flows through the road.
  • the air conditioning system is composed of four main parts: compressor 1, condenser 2, throttling device, and evaporator 4.
  • the working fluid is circulated and connected by pipes in sequence to form a relatively closed system.
  • the refrigerant circulates in a fluid state in this closed refrigeration system, and achieves the purpose of air conditioning through phase change.
  • the temperature adjustment device includes a throttling module 11 and a heat exchanger 12; the first liquid inlet port of the throttling module 11 is connected to the refrigerant through a first pipe, and the first gas outlet port is connected to the exchange through a second pipe The second inlet port of the heat exchanger 12 and the second outlet port of the heat exchanger 12 are connected to the inlet port of the compressor 1 through a third pipe.
  • the throttling module 11 is used for throttling and depressurizing the incoming refrigerant; the heat exchanger 12 is used to evaporate the incoming refrigerant liquid into superheated steam to raise the suction temperature of the compressor 1.
  • the throttling module 11 includes an electronic expansion valve or an electronic throttle valve, which is used to throttle the pressure and adjust the flow rate.
  • a first one-way valve 13 is provided on the third pipe; the first one-way valve 13 controls the refrigerant to flow from the second outlet port of the heat exchanger 12 to the suction port of the compressor 1. In this way, the refrigerant is prevented from flowing in the reverse direction, affecting the normal operation of the compressor 1.
  • the first pipe of the temperature adjustment device is connected to the pipe between the condenser 2 and the throttle valve 3.
  • the refrigerant liquid discharged from the condenser 2 is divided into two paths.
  • One path absorbs heat through the throttle valve 3 to the evaporator 4 to perform a normal refrigeration cycle; the other path enters the heat exchanger 12 through the throttle module 11 to evaporate and absorb heat.
  • After becoming superheated steam, it is connected to the suction port of the compressor 1, mixed with the refrigerant discharged from the evaporator 4, and then sucked into the compressor 1.
  • a second one-way valve 5 is provided between the evaporator 4 and the suction port of the compressor 1; the second one-way valve 5 controls the flow of refrigerant from the evaporator 4 to the suction port of the compressor 1. In this way, the refrigerant is prevented from flowing in the reverse direction, affecting the normal operation of the compressor 1.
  • control device 6 for controlling the temperature adjustment device is also included.
  • the opening degree of the throttle module 11 has a corresponding relationship with the suction temperature of the compressor 1.
  • the opening degree of the throttle module 11 has a corresponding relationship with the heat exchange amount of the heat exchanger 12.
  • control device is programmed by PLC and uses PID feedback to adjust the opening of the throttle module 11.
  • a compressor 1 with an additional temperature adjustment device is used, and the first liquid inlet port of the temperature adjustment device is connected to the discharge pipe of the condenser 2 to separate the refrigerant liquid discharged from the condenser 2
  • the throttle valve 3 for normal refrigeration cycle
  • the other way through the throttle module 11 enters the heat exchanger 12 to evaporate and absorb heat, becomes superheated steam and then connects to the compressor 1 to absorb
  • the air port is mixed with the refrigerant gas discharged from the evaporator 4 and then sucked into the compressor 1.
  • the compressor 1 of the same model is selected, the system can achieve a wider temperature range and improve the use range.
  • This embodiment also provides a control device to control the opening of the throttling module 11 of the temperature control device, a program compiled by the PLC, and PID feedback to adjust the opening, improve operating efficiency, and expand the scope of application of the system reasonably.
  • Fig. 3 is a schematic structural diagram of an air conditioning system according to an exemplary embodiment
  • Fig. 4 is a schematic diagram of a control device connection of an air conditioning system according to an exemplary embodiment
  • Fig. 5 is an exemplary embodiment An example of the enthalpy diagram of an air conditioning system.
  • this embodiment provides an air conditioning system, including the above-mentioned compressor 1, the compressor 1 is connected to the condenser 2, the throttle valve 3, and the evaporator 4 in sequence to form a circulation path; the pipe Refrigerant flows through the road.
  • the air conditioning system is composed of four main parts: compressor 1, condenser 2, throttling device, and evaporator 4.
  • the working fluid is circulated and connected by pipes in sequence to form a relatively closed system.
  • the refrigerant circulates in a fluid state in this closed refrigeration system, continuously absorbs heat from the evaporator 4 through the phase change, and releases heat in the condenser 2 to achieve the purpose of cooling.
  • the temperature adjustment device includes a throttling module 11 and a heat exchanger 12; the first liquid inlet port of the throttling module 11 is connected to the refrigerant through a first pipe, and the first gas outlet port is connected to the exchange through a second pipe The second inlet port of the heat exchanger 12 and the second outlet port of the heat exchanger 12 are connected to the inlet port of the compressor 1 through a third pipe.
  • the throttling module 11 is used for throttling and depressurizing the incoming refrigerant; the heat exchanger 12 is used to evaporate the incoming refrigerant liquid into superheated steam to raise the suction temperature of the compressor 1.
  • the first pipe of the temperature adjustment device is connected to the pipe between the condenser 2 and the throttle valve 3.
  • the refrigerant liquid discharged from the condenser 2 is divided into two paths.
  • One path absorbs heat through the throttle valve 3 to the evaporator 4 to perform a normal refrigeration cycle; the other path enters the heat exchanger 12 through the throttle module 11 to evaporate and absorb heat.
  • After becoming superheated steam, it is connected to the suction port of the compressor 1, mixed with the refrigerant discharged from the evaporator 4, and then sucked into the compressor 1.
  • the discharge pipe of the condenser 2 is connected to the second liquid inlet port of the heat exchanger 12, and the second liquid outlet port of the heat exchanger 12 is connected to the throttle valve 3 through the pipe.
  • the heat exchanger 12 evaporates one way of refrigerant liquid into superheated steam and transmits it to the suction port of the compressor 1 through the pipe, while supercooling the other way of refrigerant liquid and passes it to the throttle valve 3 through the pipe to lift System capabilities and energy efficiency.
  • a second one-way valve 5 is provided between the evaporator 4 and the suction port of the compressor 1; the second one-way valve 5 controls the flow of refrigerant from the evaporator 4 to the suction port of the compressor 1. In this way, the refrigerant is prevented from flowing in the reverse direction, affecting the normal operation of the compressor 1.
  • control device 6 for controlling the throttle module 11 is also included.
  • the control device 6 includes:
  • the first unit 61 is used to control the opening of the throttle module
  • the second unit 62 is used to control the on and off of the temperature adjustment device.
  • the first unit 61 is configured to control the throttle module 11 to be turned on when the difference between the suction temperature of the compressor and the evaporation temperature is greater than the first threshold. Since the application range of the compressor 1 is limited, and the difference between the suction temperature and the evaporation temperature is greater than the first threshold, the control device controls the throttle module 11 to conduct the controllable opening.
  • the first threshold is 3-5 degrees Celsius, which may be 3, 4 or 5 degrees Celsius.
  • the first unit 61 is used to adjust the opening degree of the throttle module 11 according to the proportional relationship between the suction temperature and the opening degree of the throttle module 11.
  • the second unit 62 is configured to control the temperature adjustment device to be turned on when the air conditioning system is in the cooling mode.
  • control device is programmed by PLC and uses PID feedback to adjust the opening of the throttle module 11.
  • FIG. 5 is the pressure enthalpy diagram of the air conditioning system.
  • the second unit controls the first one-way valve to conduct, and controls the refrigerant to flow from the second outlet port of the heat exchanger 12 to the suction port of the compressor 1. In this way, the refrigerant is prevented from flowing in the reverse direction, affecting the normal operation of the compressor 1.
  • the control device controls the throttle module 11 to conduct the controllable opening.
  • the first threshold is 3-5 degrees Celsius, which may be 3, 4 or 5 degrees Celsius.
  • Q is the cooling capacity required for the cooling of the air conditioning system
  • q m1 is the refrigerant mass flow rate in the evaporator 4.
  • Q 6 is the heat exchange amount of the heat exchanger 12
  • q m1 is the mass flow rate of refrigerant in the evaporator 4.
  • q m2 is the mass flow rate of refrigerant in the temperature control device
  • H 9 is the enthalpy value of the gaseous temperature point of the refrigerant after superheating obtained from the pressure value at the second outlet port of the heat exchanger 12.
  • the throttle module 11 is selected according to the formula (2) according to the selection manual.
  • the temperature adjustment device After the temperature adjustment device is added, since the temperature adjustment device and the evaporator 4 are connected to the suction port of the compressor 1, the enthalpy value of the gas mixed at the suction port of the compressor 1 and the refrigerant flow rate q m1 in the evaporator 4, the temperature adjustment device
  • the internal refrigerant flow q m2 has a corresponding relationship;
  • q m is the mass flow rate of refrigerant sucked into the suction port of compressor 1;
  • q m1 is the mass flow rate of refrigerant in the evaporator 4.
  • q m2 is the mass flow rate of refrigerant in the temperature control device
  • H 3 is the gas enthalpy after mixing at the suction port of the compressor 1 obtained from the pressure value at the suction port of the compressor 1;
  • H 9 is the enthalpy value of the gaseous temperature point of the refrigerant after superheating obtained according to the pressure value at the outlet port of the heat exchanger 12.
  • H 3 is at least the saturation value corresponding to the suction temperature of 1 °C; control pressure enthalpy diagram to get H 3 ⁇ 397.78kJ/kg;
  • the liquid temperature point enthalpy H 9 ⁇ 426.86 kJ/kg is obtained after the liquid outlet of the condenser 2 is supercooled;
  • the second unit of the control device controls the opening degree of the throttle module 11 so that the mass flow rate of the refrigerant entering the temperature adjustment device is greater than 0.059 kg/s.
  • the opening of the throttle module 11 is proportional to the heat exchange amount of the heat exchanger 12, the greater the heat exchange amount of the heat exchanger 12, the refrigerant mass flow rate in the temperature adjustment device The higher the value, the greater the opening of the throttle module 11.
  • the opening of the throttle module 11 is inversely proportional to the suction temperature of the compressor 1, the higher the suction temperature of the compressor 1, the refrigerant in the temperature adjustment device The lower the mass value, the smaller the opening degree of the throttle module 11.
  • the diameter of the first pipe has a corresponding relationship with the heat exchange amount of the heat exchanger 12. According to the above data of the air conditioning system, the refrigerant flow rate in the first pipe can be obtained:
  • D 1 is the diameter of the first pipeline
  • q m2 is the mass flow rate of refrigerant in the temperature control device
  • the first pipeline is a DN10 tube.
  • the theoretical value of the first pipe diameter D 1 obtained from the suction temperature of the compressor 1 and the heat exchange capacity of the heat exchanger 12 is at least 6 mm, and the loss needs to be considered in actual operation.
  • the diameter of the first pipe is proportional to the heat exchange amount of the heat exchanger 12, the higher the heat exchange amount of the heat exchanger 12, the more the mass flow rate of refrigerant in the temperature adjustment device The higher, the larger the diameter of the first pipe.
  • the diameter of the second pipe has a corresponding relationship with the heat exchange amount of the heat exchanger 12.
  • the refrigerant flow in the second pipe can be obtained:
  • D 2 is the diameter of the second pipeline
  • v 2 is the refrigerant flow rate in the second pipe
  • q m2 is the mass flow rate of refrigerant in the temperature control device
  • the second pipe is DN15 pipe.
  • the theoretical value of the second pipe diameter D 2 according to the suction temperature of the compressor 1 and the heat exchange capacity of the heat exchanger 12 is at least 12.8 mm, and the loss needs to be considered in actual operation.
  • the diameter of the second pipe is proportional to the heat exchange amount of the heat exchanger 12, the higher the heat exchange amount of the heat exchanger 12, the more the mass flow rate of refrigerant in the temperature adjustment device The higher, the larger the diameter of the second pipe.
  • the diameter of the third pipe has a corresponding relationship with the heat exchange amount of the heat exchanger 12.
  • the third pipe and the second pipe use the same pipe diameter.
  • a compressor 1 with an additional temperature adjustment device is used, and the intake end of the temperature adjustment device is connected to the discharge pipe of the condenser 2 to divide the refrigerant liquid discharged from the condenser 2 into two After passing through the heat exchanger 12 for supercooling all the way, the throttle valve 3 to the evaporator 4 absorbs heat for a more efficient refrigeration cycle; the other path enters the heat exchanger 12 through the throttle module 11 to evaporate and absorb heat, changing After the superheated steam is formed, it is connected to the suction port of the compressor 1, mixed with the refrigerant gas discharged from the evaporator 4, and then sucked into the compressor 1.
  • This embodiment also provides a control device to control the opening of the throttling module 11 of the temperature control device, a program compiled by PLC, and PID feedback to adjust the opening, improve operating efficiency, and expand the scope of application of the system.

Abstract

一种压缩机（1），包括压缩机本体，还包括用于调节压缩机（1）吸气温度的调温装置，调温装置包括节流模块（11）和换热器（12），节流模块（11）的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接换热器（12）的第二进气端口，换热器（12）的第二出气端口通过第三管道接入压缩机（1）的吸气口。通过在压缩机（1）的吸气口增设一路调温装置，当空气调节系统进行制冷时，通过节流模块（11）连接管路接入制冷剂，经换热器（12）调温后与蒸发器（4）输出的气体混合接入压缩机（1）吸气口，解决超出压缩机（1）使用范围的使用问题。

Description

一种压缩机、空气调节系统
本申请基于申请号为201811457293.0、申请日为2018年11月30日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本发明涉及压缩机技术领域，特别涉及一种压缩机、空气调节系统。
背景技术
在蒸气压缩式制冷机组中，压缩机是制冷系统的心脏，制冷机组的运行范围直接取决于压缩机的运行范围，受限于压缩机的使用极限，所以蒸发器中不能获取更低的蒸发温度，以免压缩机吸入过低温度的制冷剂造成压缩机的损坏。
现有技术中，一种中间补气制冷循环方法，通过在螺杆压缩机压缩工质过程中开设一个补气口，让一部分冷凝后的制冷剂液体经过节流阀降压在经济器换热后产生的制冷剂蒸气通过该补气口进入压缩机继续被压缩，相当于两次压缩，但通过在压缩机的中间进行补气，虽然能提高压缩机的能效，但仍无法解决其实际运行温度范围的问题。
发明内容
本发明实施例提供了一种压缩机、空气调节系统，以扩展压缩机的适用范围。为了对披露的实施例的一些方面有一个基本的理解，下面给出了简单的概括。该概括部分不是泛泛评述，也不是要确定关键/重要组成元素或描绘这些实施例的保护范围。其唯一目的是用简单的形式呈现一些概念，以此作为后面的详细说明的序言。
根据本发明实施例的第一方面，提供了一种压缩机。
在一些可选实施例中，所述压缩机，包括压缩机本体，还包括用于调节所述压缩机吸气温度的调温装置；
所述调温装置包括节流模块、换热器；所述节流模块的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接所述换热器的第二进气端口，所述换热器的第二出气端口通过第三管道接入所述压缩机的吸气口。
在一些可选实施例中，所述第三管道上设有第一单向阀；所述第一单向阀控制制冷剂由所述换热器的第二出气端口流向所述压缩机吸气口。
根据本发明实施例的第二方面，提供了一种空气调节系统。
在一些可选实施例中，所述空气调节系统包括上述的压缩机，所述压缩机与冷凝器、节流阀、蒸发器依次连接管路，构成循环通路；所述管路中流通有制冷剂；所述调温装置的第一管道接入所述冷凝器与所述节流阀之间的管道，或，所述调温装置的第一管道接入 制冷剂输入管道。
在一些可选实施例中，还包括用于控制所述调温装置的控制装置。
在一些可选实施例中，所述控制装置包括：第一单元，用于控制所述节流模块的开度；第二单元，用于控制所述调温装置的导通与截止。
本发明实施例提供的技术方案可以包括以下有益效果：
本发明提供的一种压缩机、空气调节系统，在压缩机的吸气口增设一路调温装置，当该空气调节系统进行制冷时，通过节流模块连接管路接入制冷剂，经换热器调温后与蒸发器输出的气体混合接入压缩机吸气口，实现在原有的压缩机适用范围上进行扩展，有效解决了超出压缩机使用范围的使用问题。
应当理解的是，以上的一般描述和后文的细节描述仅是示例性和解释性的，并不能限制本发明。
附图说明
此处的附图被并入说明书中并构成本说明书的一部分，示出了符合本发明的实施例，并与说明书一起用于解释本发明的原理。
图1是根据一示例性实施例示出的一种压缩机的结构示意图；
图2是根据一示例性实施例示出的一种空气调节系统的结构示意图；
图3是根据一示例性实施例示出的一种空气调节系统的结构示意图；
图4是根据一示例性实施例示出的一种空气调节系统的控制装置连接示意图；
图5是根据一示例性实施例示出的一种空气调节系统的压焓图；
其中，1-压缩机，11-节流模块，12-换热器，13-第一单向阀，2-冷凝器，3-节流阀，4-蒸发器，5-第二单向阀，6-控制装置，61-第一单元，62-第二单元。
具体实施方式
以下描述和附图充分地示出本文的具体实施方案，以使本领域的技术人员能够实践它们。一些实施方案的部分和特征可以被包括在或替换其他实施方案的部分和特征。本文的实施方案的范围包括权利要求书的整个范围，以及权利要求书的所有可获得的等同物。本文中，术语“第一”、“第二”等仅被用来将一个元素与另一个元素区分开来，而不要求或者暗示这些元素之间存在任何实际的关系或者顺序。实际上第一元素也能够被称为第二元素，反之亦然。而且，术语“包括”、“包含”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的结构、装置或者设备不仅包括那些要素，而且还包括没有明确列出的其他要素，或者是还包括为这种结构、装置或者设备所固有的要素。在没有更多限制的情况下，由语句“包括一个……”限定的要素，并不排除在包括所述要素的结构、装置或者设备中还存在另外的相同要素。本文中各个实施例采用递进的方式描述，每个实施例重点说明的都是与其他实施例的不同之处，各个实施例之间相同相似部分互相 参见即可。
本文中的术语“纵向”、“横向”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本文和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。在本文的描述中，除非另有规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是机械连接或电连接，也可以是两个元件内部的连通，可以是直接相连，也可以通过中间媒介间接相连，对于本领域的普通技术人员而言，可以根据具体情况理解上述术语的具体含义。
本文中，除非另有说明，术语“多个”表示两个或两个以上。
本文中，字符“/”表示前后对象是一种“或”的关系。例如，A/B表示：A或B。
本文中，术语“和/或”是一种描述对象的关联关系，表示可以存在三种关系。例如，A和/或B，表示：A或B，或，A和B这三种关系。
图1是根据一示例性实施例示出的一种压缩机1的结构示意图。
如图1所示，本实施例提供一种压缩机，包括压缩机本体，还包括用于调节该压缩机吸气温度的调温装置；本实施例中，制冷剂通过调温装置进行温度调节后，与正常进入压缩机1吸气口的气体混合，以提高压缩机1吸气温度。
可选的，该调温装置包括节流模块11、换热器12；该节流模块11的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接该换热器12的第二进气端口，该换热器12的第二出气端口通过第三管道接入压缩机1吸气口。如此，节流模块11用于将通入的制冷剂进行节流降压；换热器12用于将通入的制冷剂液体蒸发成过热蒸汽，提升压缩机1的吸气温度。
可选的，该节流模块11包括电子膨胀阀或电子调流阀，用于进行节流降压，调节流量。
可选的，该第三管道上设有第一单向阀13；该第一单向阀13控制制冷剂由该换热器12的第二出气端口流向该压缩机1吸气口。如此，防止制冷剂反方向流动，影响压缩机1正常工作。
采用图1示出的可选实施例，在压缩机1的吸气口后增加一路调温装置，通过对制冷剂进行节流调压，经换热器12蒸发升温后，与其他气体混合通入压缩机1吸气口，扩展了压缩机的适用范围。
在其他可选实施例中，该调温装置的节流模块11通过第一管道接入制冷剂，该制冷剂可以是自冷凝器排出的制冷剂液体，经节流模块11节流降压后进入换热器12成为过热蒸汽，也可以是从其他任何管路接入的制冷剂、气体，进入换热器12进行换热调温，然后通至压缩机1吸气口，以扩展空气调节系统原有压缩机1使用范围。
图2是根据一示例性实施例示出的一种空气调节系统的结构示意图。
如图2所示，本实施例提供一种空气调节系统，包括上述压缩机1，该压缩机1与冷凝器2、节流阀3、蒸发器4依次连接管路，构成循环通路；该管路中流通有制冷剂。
在本实施例中，空气调节系统是由压缩机1、冷凝器2、节流装置、蒸发器4四个主要部分组成，工质循环其中，用管道依次连接，形成一个相对封闭的系统。进行制冷模式时，制冷剂在这个封闭的制冷系统中以流体状态循环，通过相变，实现空气调节的目的。
可选的，该调温装置包括节流模块11、换热器12；该节流模块11的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接该换热器12的第二进气端口，该换热器12的第二出气端口通过第三管道接入压缩机1吸气口。如此，节流模块11用于将通入的制冷剂进行节流降压；换热器12用于将通入的制冷剂液体蒸发成过热蒸汽，提升压缩机1的吸气温度。
可选的，该节流模块11包括电子膨胀阀或电子调流阀，用于进行节流降压，调节流量。
可选的，该第三管道上设有第一单向阀13；该第一单向阀13控制制冷剂由该换热器12的第二出气端口流向该压缩机1吸气口。如此，防止制冷剂反方向流动，影响压缩机1正常工作。
可选的，该调温装置的第一管道接入该冷凝器2与节流阀3之间的管道。如此，冷凝器2排出的制冷剂液体分为两路，一路经节流阀3至蒸发器4吸热，进行正常制冷循环；另一路经节流模块11进入换热器12内蒸发吸热，变成过热蒸汽后接入压缩机1吸气口，与蒸发器4排出的制冷剂混合后，被吸入压缩机1。
可选的，该蒸发器4与该压缩机1吸气口之间设有第二单向阀5；该第二单向阀5控制制冷剂由该蒸发器4流向压缩机1吸气口。如此，防止制冷剂反方向流动，影响压缩机1正常工作。
可选的，还包括用于控制该调温装置的控制装置6。
可选的，该节流模块11的开度与该压缩机1的吸气温度具有对应关系。
可选的，该节流模块11的开度与该换热器12的换热量具有对应关系。
可选的，该控制装置通过PLC编程，利用PID反馈对该节流模块11进行开度调节。
采用图2示出的可选实施例，采用增设调温装置的压缩机1，并将调温装置的第一进液端口连接至冷凝器2排出管道，将冷凝器2排出的制冷剂液体分为两路，一路经节流阀3至蒸发器4吸热，进行正常制冷循环；另一路经节流模块11进入换热器12内蒸发吸热，变成过热蒸汽后接入压缩机1吸气口，与蒸发器4排出的制冷剂气体混合后，被吸入压缩机1。相比于常规的空气调节系统，选取同一个型号的压缩机1，本系统可以取得更广温度范围，提高了使用范围。本实施例还提供了通过控制装置，对调温装置的节流模块11进行开度控制，通过PLC编制程序，利用PID反馈进行调节开度，提高运行效率，合理的扩展系统的适用范围。
图3是根据一示例性实施例示出的一种空气调节系统的结构示意图；图4是根据一示 例性实施例示出的一种空气调节系统的控制装置连接示意图；图5是根据一示例性实施例示出的一种空气调节系统的压焓图。
如图3所示，本实施例提供一种空气调节系统，包括上述压缩机1，该压缩机1与冷凝器2、节流阀3、蒸发器4依次连接管路，构成循环通路；该管路中流通有制冷剂。
在本实施例中，空气调节系统是由压缩机1、冷凝器2、节流装置、蒸发器4四个主要部分组成，工质循环其中，用管道依次连接，形成一个相对封闭的系统。进行制冷模式时，制冷剂在这个封闭的制冷系统中以流体状态循环，通过相变，连续不断地从蒸发器4中吸取热量，并在冷凝器2中放出热量，从而实现制冷的目的。
可选的，该调温装置包括节流模块11、换热器12；该节流模块11的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接该换热器12的第二进气端口，该换热器12的第二出气端口通过第三管道接入压缩机1吸气口。如此，节流模块11用于将通入的制冷剂进行节流降压；换热器12用于将通入的制冷剂液体蒸发成过热蒸汽，提升压缩机1的吸气温度。
可选的，该调温装置的第一管道接入该冷凝器2与节流阀3之间的管道。如此，冷凝器2排出的制冷剂液体分为两路，一路经节流阀3至蒸发器4吸热，进行正常制冷循环；另一路经节流模块11进入换热器12内蒸发吸热，变成过热蒸汽后接入压缩机1吸气口，与蒸发器4排出的制冷剂混合后，被吸入压缩机1。
可选的，所以冷凝器2的排出管道连接该换热器12的第二进液端口，该换热器12的第二出液端口通过管道连接节流阀3。如此，该换热器12在将一路制冷剂液体蒸发成过热蒸汽通过管道传递至压缩机1吸气口的同时，将另一路制冷剂液体进行过冷后经管道传递至节流阀3，提升系统的能力和能效。
可选的，该蒸发器4与该压缩机1吸气口之间设有第二单向阀5；该第二单向阀5控制制冷剂由该蒸发器4流向压缩机1吸气口。如此，防止制冷剂反方向流动，影响压缩机1正常工作。
可选的，还包括用于控制该节流模块11的控制装置6。如图4所示，该控制装置6包括：
第一单元61，用于控制该节流模块的开度；
第二单元62，用于控制该调温装置的导通与截止。
可选的，第一单元61，用于当该压缩机吸气温度与蒸发温度的差值大于第一阈值时，控制该节流模块11导通。由于压缩机1适用范围受限，吸气温度与蒸发温度的差值大于第一阈值，控制装置控制该节流模块11进行开度可控的导通。可选的，该第一阈值为3-5摄氏度，可以是3、4或5摄氏度。
可选的，第一单元61，用于根据该吸气温度与该节流模块11开度之间的比例关系，调节该节流模块11的开度。
可选的，该吸气温度与该节流模块11开度之间为负相关比例关系。
可选的，第二单元62，用于当该空气调节系统运行制冷模式时，控制该调温装置导通。
可选的，该控制装置通过PLC编程，利用PID反馈对该节流模块11进行开度调节。
具体的，以所需制冷量Q＝200kW，蒸发器4出水温度为2℃，进水温度为30℃，压缩机1吸气温度T≥1℃的图3所示空气调节系统为例，对该控制装置6进行说明。图5为该空气调节系统的压焓图。
根据该空气调节系统，设计蒸发温度T 0＝-2℃，冷凝温度T c＝37℃。
当该空气调节系统进行制冷时，第二单元控制第一单向阀导通，控制制冷剂由该换热器12的第二出气端口流向该压缩机1吸气口。如此，防止制冷剂反方向流动，影响压缩机1正常工作。
由于压缩机1适用范围受限，吸气温度与蒸发温度的差值大于第一阈值，控制装置控制该节流模块11进行开度可控的导通。可选的，该第一阈值为3-5摄氏度，可以是3、4或5摄氏度。
根据蒸发温度、冷凝温度获取蒸发器4内制冷剂质量流量q m1
Q＝q m1×(H 2-H 1)   …(1)
其中，Q为空气调节系统制冷所需制冷量；
q m1为蒸发器4内制冷剂质量流量；
H 1为蒸发器4入口焓值，根据蒸发器4入口处压力值，对照压焓图得到本系统中H 1＝241.52kJ/kg；
H 2为蒸发器4出口焓值，根据蒸发器4出口处压力值，对照压焓图得到本系统中H 2＝396.45kJ/kg；
则，根据式(1)获取该蒸发器4内制冷剂流量q m1＝1.29kg/s。
增设调温装置，以该调温装置的换热器12能增加过冷度5℃进行控制，获取换热器12的换热量Q 6；
Q 6＝q m2×(H 9-H 6)＝q m1×(H 5-H 7)   …(2)
其中，Q 6为换热器12的换热量；
q m1为蒸发器4内制冷剂的质量流量；
q m2为调温装置内制冷剂的质量流量；
H 5为根据冷凝器2出液端口处压力值得到的饱和液态温度点焓值，对照压焓图得到本系统中H 5＝251.7kJ/kg；
H 6为根据节流模块11第一出气端口处压力值得到的焓值，对照压焓图得到本系统中H 6＝251.7kJ/kg；
H 7为根据换热器12第二出液端口处压力值得到的制冷剂过冷后液态温度点焓值，对照压焓图得到本系统中H 7＝244.17kJ/kg；
H 9为根据换热器12第二出气端口处压力值得到的制冷剂过热后气态温度点焓值。
根据式(1)获取q m1＝1.29kg/s，得到换热器12的换热量Q 6＝9.71kW。
根据式(2)获取
Figure PCTCN2019105336-appb-000001
可选的，根据式(2)对照选型手册选择节流模块11。
增设调温装置后，由于调温装置与蒸发器4均接入压缩机1吸气口，压缩机1吸气口处混合后气体焓值与蒸发器4内制冷剂流量q m1、调温装置内制冷剂流量q m2均具有相对应关系；
q m＝q m1+q m2   …(4)
q m×H 3＝q m1×H 2+q m2×H 9   …(5)
其中，q m为压缩机1吸气口吸入制冷剂的质量流量；
q m1为蒸发器4内制冷剂的质量流量；
q m2为调温装置内制冷剂的质量流量；
H 2为蒸发器4出气端口焓值，根据蒸发器4出气端口处压力值，对照压焓图得到本系统中H 2＝396.45kJ/kg；
H 3为根据压缩机1吸气口处压力值得到的压缩机1吸气口处混合后气体焓值；
H 9为根据换热器12出气端口处压力值得到的制冷剂过热后气态温度点焓值。
根据式(4)、式(5)获取压缩机1吸气口处混合后气体焓值
Figure PCTCN2019105336-appb-000002
根据压缩机1吸气温度T≥1℃，H 3至少为吸气温度为1℃时对应的饱和值；对照压焓图得到H 3≥397.78kJ/kg；
由式(6)得到冷凝器2出液口过冷后液态温度点焓值H 9≥426.86kJ/kg；
由式(3)得到q m2≥0.059kg/s。
即，根据PLC编程使得该情况下控制装置的第二单元对节流模块11进行开度控制，满足进入调温装置的制冷剂的质量流量大于0.059kg/s。
由式(3)可知，该节流模块11的开度与该换热器12的换热量成正比，该换热器12的换热量越大，该调温装置内的制冷剂质量流量数值越高，该节流模块11的开度越大。
由式(3)与式(6)可知，该节流模块11的开度与该压缩机1的吸气温度成反比，该压缩机1的吸气温度越高，该调温装置内制冷剂质量数值越低，该节流模块11的开度越小。
可选的，该第一管道的管径与该换热器12的换热量具有对应关系。根据上述空气调节系统的各项数据，可得第一管道内制冷剂流量：
Figure PCTCN2019105336-appb-000003
其中，D 1为第一管道的管径；
v 1为第一管道内制冷剂流速，该制冷剂流速为1.2～3m/s，可以是1.5m/s，2m/s或3m/s，本实施例中v 1＝1.5m/s；
q m2为调温装置内制冷剂的质量流量；
V l1为第一管道内饱和液比体积，第一管道流通制冷剂为低温液体，按饱和液态查压焓图，得到V l1＝0.862dm/kg；
当q m2＝0.059kg/s时，由式(7)得到D 1≈6mm。可选的，该第一管道选用DN10管。如此，根据压缩机1吸气温度、换热器12换热量得到第一管道管径D 1的理论数值至少为6mm，实际运行中需考虑损耗。
由式(7)可知，该第一管道的管径与该换热器12的换热量成正比，该换热器12的换热量越高，该调温装置内制冷剂质量流量数值越高，该第一管道的管径越大。
可选的，该第二管道的管径与该换热器12的换热量具有对应关系。
根据上述空气调节系统各项数据，可得第二管道内制冷剂流量：
Figure PCTCN2019105336-appb-000004
其中，D 2为第二管道的管径；
v 2为第二管道内制冷剂流速，
q m2为调温装置内制冷剂的质量流量；
V g2为第一管道内饱和气比体积，第二管道内流通的制冷剂经过节流模块11后成为低温气体，按饱和气态查压焓图，得到V g2＝0.02162dm/kg；
当q m2＝0.059kg/s时，由式(7)得到D 2≈12.8mm。选的，该第二管道选用DN15管。如此，根据压缩机1吸气温度、换热器12换热量得到第二管道管径D 2的理论数值至少为12.8mm，实际运行中需考虑损耗。
由式(8)可知，该第二管道的管径与该换热器12的换热量成正比，该换热器12的换热量越高，该调温装置内制冷剂质量流量数值越高，该第二管道的管径越大。
可选的，该第三管道的管径与该换热器12的换热量具有对应关系。
可选的，该第三管道与该第二管道采用相同管径。
采用图3示出的可选实施例，采用增设调温装置的压缩机1，并将调温装置的进气端连接至冷凝器2排出管道，将冷凝器2排出的制冷剂液体分为两路，一路经换热器12进行过冷后，经节流阀3至蒸发器4吸热，进行更高效的制冷循环；另一路经节流模块11进入换热器12内蒸发吸热，变成过热蒸汽后接入压缩机1吸气口，与蒸发器4排出的制冷剂气体混合后，被吸入压缩机1。相比于常规的空气调节系统，选取同一个型号的压缩机1，本系统可以取得更广温度范围，提高了使用范围。本实施例还提供了通过控制装置，对调温装置的节流模块11进行开度控制，通过PLC编制程序，利用PID反馈进行调节开度，提高运行效率，合理的扩展系统的适用范围。
本发明并不局限于上面已经描述并在附图中示出的结构，并且可以在不脱离其范围进 行各种修改和改变。本发明的范围仅由所附的权利要求来限制。

Claims (10)

  1. 一种压缩机，包括压缩机本体，其特征在于，还包括用于调节所述压缩机吸气温度的调温装置；
    所述调温装置包括节流模块、换热器；所述节流模块的第一进液端口通过第一管道接入制冷剂，第一出气端口通过第二管道连接所述换热器的第二进气端口，所述换热器的第二出气端口通过第三管道接入所述压缩机的吸气口。
  2. 根据权利要求1所述的压缩机，其特征在于，所述第三管道上设有第一单向阀；所述第一单向阀控制制冷剂由所述换热器的第二出气端口流向所述压缩机吸气口。
  3. 一种空气调节系统，其特征在于，包括权利要求1或2所述的压缩机，所述压缩机与冷凝器、节流阀、蒸发器依次连接管路，构成循环通路；所述管路中流通有制冷剂；所述调温装置的第一管道接入所述冷凝器与所述节流阀之间的管道，或，所述调温装置的第一管道接入制冷剂输入管道。
  4. 根据权利要求3所述的空气调节系统，其特征在于，所述蒸发器与所述压缩机之间设有第二单向阀；所述第二单向阀控制制冷剂由所述蒸发器流向所述压缩机吸气口。
  5. 根据权利要求3所述的空气调节系统，其特征在于，还包括用于控制所述调温装置的控制装置。
  6. 根据权利要求5所述的空气调节系统，其特征在于，所述控制装置包括：
    第一单元，用于控制所述节流模块的开度；
    第二单元，用于控制所述调温装置的导通与截止。
  7. 根据权利要求6所述的空气调节系统，其特征在于，所述第一单元，用于当所述压缩机吸气温度与蒸发温度的差值大于第一阈值时，控制所述节流模块导通。
  8. 根据权利要求7所述的空调调节系统，其特征在于，所述第一单元，用于根据所述吸气温度与所述节流模块开度之间的比例关系，调节所述节流模块的开度。
  9. 根据权利要求8所述的空气调节系统，其特征在于，所述吸气温度与所述节流模块开度之间为负相关比例关系。
  10. 根据权利要求6所述的空气调节系统，其特征在于，所述第二单元，用于当所述空气调节系统运行制冷模式时，控制所述调温装置导通。
PCT/CN2019/105336 2018-11-30 2019-09-11 一种压缩机、空气调节系统 WO2020108005A1 (zh)

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