阅读说明：本技术 压缩机的测试方法、装置、设备、系统及计算机可读存储介质 (Compressor testing method, device, equipment, system and computer readable storage medium ) 是由 卢耀汕 廖四清 阚望 曾令华 尚凯锋 区永东 于 2021-09-23 设计创作，主要内容包括：本申请提供了一种压缩机的测试方法、装置、设备、系统及计算机可读存储介质。压缩机的测试方法,包括：获取压缩机的实际吸气干度；根据所述实际吸气干度和目标吸气干度调节电子膨胀阀开度和蒸发器所在量热桶内加热器的输出功率,以使所述实际吸气干度与所述目标吸气干度之间的吸气干度差值的绝对值与所述目标吸气干度之比在设定范围内；测试所述压缩机的性能参数。本申请的压缩机的测试方法,可以准确使实际吸气干度与目标吸气干度之间的吸气干度差值的绝对值与目标吸气干度之比在设定范围内,进而准确测试出压缩机的性能参数。(The application provides a method, a device, equipment, a system and a computer readable storage medium for testing a compressor. A method of testing a compressor, comprising: acquiring actual suction dryness of the compressor; adjusting the opening of an electronic expansion valve and the output power of a heater in a calorimetric bucket where an evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range; and testing performance parameters of the compressor. The testing method of the compressor can accurately enable the ratio of the absolute value of the suction dryness difference value between the actual suction dryness and the target suction dryness to be within the set range, and further accurately test the performance parameters of the compressor.)

1. A method of testing a compressor, comprising:

acquiring actual suction dryness of the compressor;

adjusting the opening of an electronic expansion valve and the output power of a heater in a calorimetric bucket where an evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range;

and testing performance parameters of the compressor.

2. The method for testing a compressor according to claim 1, wherein said obtaining an actual dryness of suction of the compressor comprises:

and calculating the actual air suction dryness according to the output power of a heater in the calorimetric barrel where the evaporator is positioned, the input power of the compressor, the mass flow of the refrigerant, the heat dissipation capacity of a shell of the compressor to the environment, the exhaust enthalpy value of the compressor, the air suction enthalpy value of the compressor, the outlet enthalpy value of the condenser, the saturated liquid enthalpy value of the evaporator and the saturated gas enthalpy value of the evaporator.

3. The method for testing a compressor of claim 1, further comprising:

calculating the power initial value of the output power of a heater in a calorimetric bucket where the evaporator is located and the flow initial value of the refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated gas enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the condenser outlet enthalpy value;

calculating an opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow;

and controlling the opening of the electronic expansion valve to be the initial opening value, and controlling the output power of the heater in the calorimetric bucket where the evaporator is located to be the initial power value.

4. The method for testing a compressor according to claim 3, wherein the adjusting of the opening of the electronic expansion valve and the output power of the heater in the thermotub where the evaporator is located according to the actual air quality and the target air quality comprises:

calculating an inspiratory quality difference between the target inspiratory quality and the actual inspiratory quality;

calculating a ratio of an absolute value of the inspiratory quality difference to the target inspiratory quality;

calculating a target exhaust temperature by adopting an interpolation method according to the intake dryness difference value, the two groups of actual intake dryness and the actual exhaust temperature;

calculating the opening target value of the opening of the electronic expansion valve after adjustment and the power target value of the output power of the heater in the calorimetric bucket where the evaporator is located;

controlling the opening degree of the electronic expansion valve to be adjusted to the target opening degree value, and controlling the output power of a heater in the calorimetric barrel where the evaporator is located to be adjusted to the target power value;

acquiring actual suction dryness and actual exhaust temperature of a compressor;

and returning to the step of calculating the inspiration dryness difference between the target inspiration dryness and the actual inspiration dryness until the ratio of the absolute value of the inspiration dryness difference to the target inspiration dryness is within a set range.

5. The method for testing a compressor of claim 3, wherein said compressor isentropic efficiency is calculated based on a target isentropic discharge enthalpy value, a compressor discharge enthalpy value, and a compressor suction enthalpy value.

6. A method for testing a compressor according to any one of claims 1 to 5, wherein the set range is 0.1% to 2%.

7. A testing apparatus of a compressor, comprising:

the acquisition module is used for acquiring the actual suction dryness of the compressor;

the adjusting module is used for adjusting the opening of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range;

and the testing module is used for testing the performance parameters of the compressor.

8. The testing apparatus of a compressor according to claim 7, further comprising:

the calculation module is used for calculating the power initial value of the output power of a heater in the caloric barrel where the evaporator is located and the flow initial value of the refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated air enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the outlet enthalpy value of the condenser; calculating an opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow;

and the control module is used for controlling the opening of the electronic expansion valve to be the initial opening value and controlling the output power of the heater in the calorimetric barrel where the evaporator is located to be the initial power value.

9. The testing apparatus of a compressor according to claim 8, wherein the adjusting module comprises:

a calculation unit for calculating an inspiratory quality difference between the target inspiratory quality and the actual inspiratory quality, and calculating a ratio of an absolute value of the inspiratory quality difference to the target inspiratory quality;

the adjusting unit is used for calculating a target exhaust temperature by adopting an interpolation method according to the air suction dryness difference value, the two groups of actual air suction dryness and the actual exhaust temperature, and calculating an opening target value of the opening of the electronic expansion valve and a power target value of the output power of the heater in the calorimetric barrel where the evaporator is located after adjustment;

the control unit is used for controlling the opening degree of the electronic expansion valve to be adjusted to the target opening degree value and controlling the output power of the heater in the calorimetric barrel where the evaporator is located to be adjusted to the target power value;

and the judging unit is used for judging whether the ratio of the absolute value of the air suction dryness difference value to the target air suction dryness reaches the set range.

10. The testing system of the compressor is characterized by comprising a condenser, a dryer, a subcooler, a filter, an electronic expansion valve, an evaporator and a heat measuring barrel, wherein the evaporator is arranged in the heat measuring barrel; the condenser, the dryer, the subcooler, the filter, the electronic expansion valve and the evaporator are sequentially connected, the outlet of the evaporator is used for being connected with the air suction port of the compressor, and the inlet of the condenser is used for being connected with the air exhaust port of the compressor; the testing system of the compressor is used for controlling and testing the compressor according to the testing method of the compressor of any one of claims 1 to 6.

11. A test apparatus of a compressor comprising a memory, a processor and a computer program stored in the memory and executable on the processor, characterized in that the processor implements a test method of a compressor according to any one of claims 1 to 6 when executing the computer program.

12. A computer-readable storage medium, in which a computer program is stored, which, when being executed by a processor, carries out a method for testing a compressor according to any one of claims 1 to 6.

Technical Field

The present application relates to the field of compressor technologies, and in particular, to a method, an apparatus, a device, a system and a computer readable storage medium for testing a compressor.

Background

At present, the device for testing the refrigerating capacity of the compressor can test performance parameters of the compressor, such as the refrigerating capacity, power, energy efficiency and the like of the compressor. However, in the testing condition, it is necessary to ensure that the suction gas of the compressor has a certain superheat degree, and the compressor can be stably operated only when the suction gas temperature is generally higher than the evaporation temperature by more than 5 ℃, and then the test is performed. And to the operating mode of the liquid of area of inhaling, no matter how much liquid absorption capacity, the suction temperature all is the same with evaporimeter temperature, so cause the device because of can't differentiate the quality of inspiration (or the liquid absorption capacity) of compressor, lead to the performance parameter of compressor under the operating mode of the liquid of area of inhaling leads to testing. It is currently proposed to stabilize the compressor to a target suction dryness by adjusting the output power of the thermal bucket heater and then test the performance parameters of the compressor. However, for part of the refrigerant (such as R32), the output power of the calorimetric bucket heater is not in a linear relationship with the suction dryness, so that the test result lacks uniqueness, and the performance parameters of the compressor are difficult to accurately test.

Disclosure of Invention

An object of the embodiments of the present application is to provide a method, an apparatus, a device, a system and a computer readable storage medium for testing a compressor, so as to solve the problem that in the prior art, when a refrigeration capacity of a compressor is tested, because output power of a heater of a calorimetric barrel and a suction dryness are not in a linear relationship, a test result lacks uniqueness, and a performance parameter of the compressor is difficult to accurately test.

In a first aspect, an embodiment of the present application provides a testing method for a compressor, including:

acquiring actual suction dryness of the compressor;

adjusting the opening of an electronic expansion valve and the output power of a heater in a calorimetric bucket where an evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range;

and testing performance parameters of the compressor.

In a possible implementation manner of the first aspect, the actual air suction dryness of the compressor is obtained, and the opening of the electronic expansion valve and the output power of the heater in the calorimetric tank where the evaporator is located are adjusted according to the actual air suction dryness and the target air suction dryness.

In an alternative embodiment, the obtaining the actual dryness of the suction gas of the compressor includes:

and calculating the actual air suction dryness according to the output power of a heater in the calorimetric barrel where the evaporator is positioned, the input power of the compressor, the mass flow of the refrigerant, the heat dissipation capacity of the shell of the compressor to the environment, the exhaust enthalpy value of the compressor, the air suction enthalpy value of the compressor, the outlet enthalpy value of the condenser, the saturated liquid enthalpy value of the evaporator and the saturated gas enthalpy value of the evaporator.

In an alternative embodiment, the method for testing a compressor further comprises:

calculating the power initial value of the output power of a heater in a calorimetric bucket where the evaporator is located and the flow initial value of the refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated gas enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the condenser outlet enthalpy value;

calculating an opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow;

and controlling the opening of the electronic expansion valve to be the initial opening value, and controlling the output power of the heater in the calorimetric bucket where the evaporator is located to be the initial power value.

In an alternative embodiment, the adjusting the opening of the electronic expansion valve and the output power of the heater in the heating barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness comprises:

calculating an inspiratory quality difference between the target inspiratory quality and the actual inspiratory quality;

calculating a ratio of an absolute value of the inspiratory quality difference to the target inspiratory quality;

calculating a target exhaust temperature by adopting an interpolation method according to the intake dryness difference value, the two groups of actual intake dryness and the actual exhaust temperature;

calculating the opening target value of the opening of the electronic expansion valve after adjustment and the power target value of the output power of the heater in the calorimetric bucket where the evaporator is located;

controlling the opening degree of the electronic expansion valve to be adjusted to the target opening degree value, and controlling the output power of a heater in the calorimetric barrel where the evaporator is located to be adjusted to the target power value;

acquiring actual suction dryness and actual exhaust temperature of a compressor;

and returning to the step of calculating the inspiration dryness difference between the target inspiration dryness and the actual inspiration dryness until the ratio of the absolute value of the inspiration dryness difference to the target inspiration dryness is within the set range.

In an alternative embodiment, the compressor isentropic efficiency is calculated based on a target isentropic discharge enthalpy value, a compressor discharge enthalpy value, and a compressor suction enthalpy value.

In an alternative embodiment, the set range is 0.1% to 2%.

In a second aspect, an embodiment of the present application provides a testing apparatus for a compressor, including:

the acquisition module is used for acquiring the actual suction dryness of the compressor;

the adjusting module is used for adjusting the opening of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range;

and the testing module is used for testing the performance parameters of the compressor.

In an alternative embodiment, the testing apparatus of the compressor further includes:

the calculation module is used for calculating the power initial value of the output power of a heater in the caloric barrel where the evaporator is located and the flow initial value of the refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated air enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the outlet enthalpy value of the condenser; calculating an opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow;

and the control module is used for controlling the opening of the electronic expansion valve to be the initial opening value and controlling the output power of the heater in the calorimetric barrel where the evaporator is located to be the initial power value.

In an alternative embodiment, the adjustment module comprises:

the calculation unit is used for calculating an inspiration dryness difference value between the target inspiration dryness and the actual inspiration dryness and then calculating the ratio of the absolute value of the inspiration dryness difference value to the target inspiration dryness;

the adjusting unit is used for calculating a target exhaust temperature by adopting an interpolation method according to the air suction dryness difference value, the two groups of actual air suction dryness and the actual exhaust temperature, and calculating an opening target value of the opening of the electronic expansion valve and a power target value of the output power of the heater in the calorimetric barrel where the evaporator is located after adjustment;

the control unit is used for controlling the opening degree of the electronic expansion valve to be adjusted to the target opening degree value and controlling the output power of the heater in the calorimetric barrel where the evaporator is located to be adjusted to the target power value;

and the judging unit is used for judging whether the ratio of the absolute value of the air suction dryness difference value to the target air suction dryness reaches the set range.

In a third aspect, an embodiment of the present application provides a testing system for a compressor, including a condenser, a dryer, a subcooler, a filter, an electronic expansion valve, an evaporator, and a heat metering barrel, where the evaporator is disposed in the heat metering barrel; the condenser, the dryer, the subcooler, the filter, the electronic expansion valve and the evaporator are sequentially connected, the outlet of the evaporator is used for being connected with the air suction port of the compressor, and the inlet of the condenser is used for being connected with the air exhaust port of the compressor; the testing system of the compressor is used for controlling and testing the compressor according to the testing method of the compressor of any one of the embodiments.

In a fourth aspect, the present application provides a testing apparatus for a compressor, which includes a memory, a processor, and a computer program stored in the memory and executable on the processor, and when the processor executes the computer program, the testing apparatus implements the testing method for a compressor according to any of the above embodiments.

In a fifth aspect, the present application provides a computer-readable storage medium, where a computer program is stored, and when the computer program is executed by a processor, the computer program implements the method for testing a compressor according to any of the above embodiments.

It is understood that the beneficial effects of the second aspect to the fifth aspect can be referred to the related description of the first aspect, and are not described herein again.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or exemplary technical descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

Fig. 1 is a schematic view of a testing system of a compressor according to a first embodiment of the present application;

FIG. 2 is a flow chart of a method for testing a compressor according to a second embodiment of the present application;

FIG. 3 is a flow chart of a portion of the steps of FIG. 2;

fig. 4 is a flowchart of a testing method of a compressor according to a third embodiment of the present disclosure;

fig. 5 is a block diagram illustrating a testing apparatus of a compressor according to a fourth embodiment of the present disclosure;

fig. 6 is a block diagram illustrating a testing apparatus of a compressor according to a fifth embodiment of the present disclosure;

fig. 7 is a block diagram of a regulating module according to a sixth embodiment of the present application;

fig. 8 is a block diagram illustrating a testing apparatus for a compressor according to a seventh embodiment of the present disclosure.

Wherein, in the drawings, the reference numerals are mainly as follows:

100-test system of compressor;

101-a condenser; 102-a dryer; 103-a subcooler; 104-a filter; 105-an electronic expansion valve; 106-an evaporator; 107-calorimetric barrel; 108-a constant temperature water tank;

200-compressor.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present application clearer, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.

In the description of the present application, "a plurality" means two or more unless specifically limited otherwise. The meaning of "a number" is one or more unless specifically limited otherwise. The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. The terms "center," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated in the drawings for convenience in describing the application and for simplicity in description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus are not to be considered limiting of the application.

In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

Reference throughout this specification to "one embodiment," "some embodiments," or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the present application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like, in various places throughout this specification are not necessarily all referring to the same embodiment, but rather "one or more but not all embodiments" unless specifically stated otherwise. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. The terms "comprising," "including," "having," and variations thereof mean "including, but not limited to," unless expressly specified otherwise.

A method, an apparatus, a device, a system, and a computer-readable storage medium for testing a compressor according to embodiments of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is a schematic view of a testing system for a compressor according to one embodiment of the present application. As shown in fig. 1, a test system 100 of a compressor includes a condenser 101, a dryer 102, a subcooler 103, a filter 104, an electronic expansion valve 105, an evaporator 106, and a heat measuring barrel 107. The evaporator 106 is placed in the calorimetric barrel 107; the condenser 101, the dryer 102, the subcooler 103, the filter 104, the electronic expansion valve 105, and the evaporator 106 are connected in this order. In test use, the outlet of the evaporator 106 is connected to the suction port of the compressor 200, and the inlet of the condenser 101 is connected to the discharge port of the compressor 200. So that the performance test of the compressor 200 is performed.

The condenser 101 controls the condensing temperature (or the discharge pressure) of the compressor 200 by controlling the flow rate of the cooling water, or the like. The dryer 102 is used to filter the moisture in the pipeline. The subcooler 103 is provided with a HEATER inside, and is also provided with a cooling water circulation, and the outlet temperature of the subcooler 103 is controlled by controlling the heating power of the HEATER. The filter 104 is disposed upstream of the electronic expansion valve 105, and is used for filtering impurities and preventing the impurities from blocking the electronic expansion valve 105. The electronic expansion valve 105 controls the throttle opening through an electric signal, thereby controlling the refrigerant mass flow and enabling the system to stably operate to a required target working condition. The evaporator 106 is arranged in a heat measuring barrel 107 with a heat preservation function, a constant temperature water tank 108 capable of realizing a constant temperature function and a HEATER are further arranged in the heat measuring barrel 107, when the compressor 200 stably operates, the refrigerating capacity of the evaporator 106 is equal to the heating power Q of the HEATER, namely the refrigerating capacity Q of the compressor 200 is measured by a thermal balance method.

In one embodiment, the testing system 100 of the compressor further comprises a flow meter for testing a total flow m of the refrigerant and oil circulating in the circulation system of the compressor 200_{General assembly}. A flow meter may be provided in the line between the filter 104 and the electronic expansion valve 105. It will be appreciated that the flow meter may also be provided on other lines of the compressor test system 100.

In one embodiment, the compressor testing system 100 further includes a sight glass for observing the flow of refrigerant in the line. A sight glass may be provided on the line between the dryer 102 and the subcooler 103 in order to observe the flow of the refrigerant in the line. It will be appreciated that the sight glass may also be provided on other lines of the compressor testing system 100.

In one embodiment, the compressor testing system 100 further includes a pressure sensor, such as may be used to detect the pressure at the suction port of the compressor 200. A pressure sensor may also be used to detect the pressure at the discharge of the compressor 200.

In one embodiment, the compressor testing system 100 further includes a temperature sensor, such as may be used to detect the temperature of the suction port of the compressor 200. A temperature sensor may also be used to detect the temperature of the discharge port of the compressor 200.

In one embodiment, the compressor testing system 100 may further include an oil separator, for example, when an oil separator is selected, the gas discharged from the compressor 200 is first separated by the oil separator, such that most of the oil discharged from the compressor 200 is directly returned to the compressor 200, and thus the amount of oil passing through the pipeline is greatly reduced.

The above are the constituent parts of the test system 100 of the compressor and the functions thereof, and the following are the procedures prepared before the test:

1. mounting the subject compressor 200: the suction port and the discharge port of the compressor 200 are respectively connected to the pipe interfaces of the test system 100 of the compressor.

2. Vacuumizing: the air inside the compressor 200 and the connection line is pumped out by the vacuum pump, preventing the compressor 200 from compressing the refrigerant containing the air.

3. Pressure maintaining: after the vacuum pumping is finished, the vacuum pump is turned off, the air tightness of the compressor 200 and the connecting pipeline is checked, and the next step is carried out after no leakage is ensured.

4. The sealed refrigerant: a refrigerant is sealed in the compressor 200 and the connection line.

5. Setting working conditions and operating parameters: inputting the type of refrigerant, the working condition (including the discharge pressure Pd (or the condensation temperature Tc), the suction pressure Ps (or the evaporation temperature Te), the suction temperature Ts (or the suction dryness Xt), the outlet temperature Tco of the condenser 101, the power specification (such as the voltage and the frequency), the displacement of the compressor 200, wherein if the compressor 200 is the inverter compressor 200, the rotation speed of the compressor 200 is also inputted.

6. Starting a test system: the testing system 100 of the compressor is used for electrifying the compressor 200 according to the set power supply specification, the compressor 200 is operated after being electrified, and the testing system enables the compressor 200 to be stabilized to the required set working condition for testing by controlling the opening degree of each water valve, the power of the heater, the opening degree of the electronic expansion valve 105 and the like.

The testing system 100 of the compressor can test the working condition that the compressor 200 has a certain suction superheat state, when the compressor 200 sucks all gas, the suction temperature Ts of the compressor 200 is greater than the evaporation temperature Te (the suction has superheat degree, and the superheat degree T is Ts-Te), and at the moment, the power of a heater in the heat measuring barrel 107 is adjusted by monitoring Ts, so that the required suction temperature Ts can be stabilized.

The testing system 100 of the compressor can also test the working condition of liquid in the air suction (i.e. when the air suction is not overheated), no matter how much the air suction dryness X is, the air suction temperature of the compressor 200 is equal to the evaporation temperature, namely Ts (Te), so that the testing system 100 of the compressor cannot judge how much the air suction dryness X is through Ts, and cannot test the working condition under a specific air suction dryness X. For example: the suction dryness X is 98 percent, the superheat degree is zero, and Te is Ts; when the suction dryness X is 95%, the suction superheat is still zero, that is, Te is Ts, so the compressor test system 100 cannot determine whether the suction dryness X is 95%, 98% or another value by the difference between the suction temperature and the evaporation temperature (i.e., the superheat).

Therefore, the invention provides a method for testing parameters such as the refrigerating capacity of the compressor 200 under the working condition that the compressor 200 sucks air and carries liquid. And the method may be implemented using the compressor testing system 100 described above.

Fig. 2 is a flowchart of a testing method of the compressor provided in this embodiment. As shown in fig. 2, the method for testing a compressor of the present embodiment includes:

and step S1, acquiring the actual air suction dryness of the compressor.

In step S1, the actual suction dryness of the compressor is the suction dryness of the compressor suction port when the compressor is operated during the test. The actual suction dryness of the compressor is obtained, and the running environment and running state of the compressor can be determined in time so as to test the performance parameters of the compressor.

In one embodiment, obtaining the actual dryness of suction of the compressor comprises: according to the output power Qc of the heater in the calorimetric bucket where the evaporator is positioned, the input power P of the compressor, the mass flow rate m of the refrigerant and the heat dissipation quantity Q of the shell of the compressor to the environment_lossCompressor discharge enthalpy value h₂Compressor suction enthalpy value h₁Enthalpy value h of outlet of condenser₃Evaporator saturated liquid enthalpy value h_liqAnd evaporator saturated air enthalpy value h_vapAnd calculating the actual inspiratory dryness X'.

The output power Qc of the heater in the heating barrel where the evaporator is located is the heating power of the heating barrel, and can be obtained by a power meter arranged on the heating barrel, for example. The compressor input power P can be obtained, for example, by a compressor power meter.

In one embodiment, the output power Qc of the heater in the calorimetric bucket and the suction enthalpy h of the compressor can be determined according to the position of the evaporator₁And the enthalpy value h of the outlet of the condenser₃And calculating the refrigerant mass flow m. For example, it can be obtained by the following formula (1).

Compressor shell heat dissipation to environment Q_lossExample ofIf the heat dissipation coefficient KA can be obtained by calculation through a formula (2) under the condition of suction superheat degree, and then Q can be obtained by calculation through a formula (3) under the condition of suction liquid_loss。

Compressor air suction port enthalpy value h₁Also called compressor suction enthalpy value h₁For example, suction superheat conditions may be determined by taking the refrigerant type and compressor suction temperature T_sPressure P of air suction inlet of compressor_sUsing a refrigerant with T_sAnd P_sH is found out from the parameter library of the corresponding relation table₁(ii) a Wherein the temperature T of the air suction port of the compressor_sThe pressure P of the air inlet of the compressor is measured by a temperature sensor arranged at the air inlet of the compressor_sMeasured by a pressure sensor arranged at the air suction port of the compressor.

The enthalpy value h of the air suction port is obtained by calculating the following formula (4) under the working condition of air suction and liquid carrying of the compressor₁′。

Enthalpy value h of air outlet of compressor₂Also called compressor discharge enthalpy value h₂E.g. by obtaining the refrigerant type and the temperature T of the compressor discharge_dPressure P of the compressor discharge port_dUsing a refrigerant with T_dAnd P_dH is found out from the parameter library of the corresponding relation table₂Wherein the temperature T of the compressor discharge port_dThe pressure P of the exhaust port of the compressor is measured by a temperature sensor arranged at the outlet of the compressor_dMeasured by a pressure sensor arranged at the outlet of the compressor.

Enthalpy value h of outlet of condenser₃E.g. by taking the refrigerant type and the temperature T at the outlet of the condenser_coPressure P of the compressor discharge port_dUsing a refrigerant with T_coAnd P_dH is found out from the parameter library of the corresponding relation table₃Wherein the temperature T of the outlet of the condenser_coMeasured by a temperature sensor arranged at the outlet of the condenser. Compressor ambient temperature T_airFor example by means of a temperature sensor arranged in the test chamber of the compressor.

Evaporator saturated liquid enthalpy value h_liqE.g. by obtaining refrigerant type, temperature T of evaporator_e(or pressure P at compressor suction port_s) Using a refrigerant with T_eOr P_sH is found out from the parameter library of the corresponding relation table_liqWherein the temperature T of the evaporator outlet_eMeasured by a temperature sensor arranged at the outlet of the evaporator.

Evaporator saturated air enthalpy value h_vapE.g. by taking the refrigerant type, the temperature T at the evaporator outlet_e(or pressure P at compressor suction port_s) Using a refrigerant with T_eOr P_sH is found out from the parameter library of the corresponding relation table_vap。

After the compressor operates stably, the parameters are obtained, and the refrigerant mass flow m is calculated according to the parameters through the following formula (1):

calculating the heat dissipation coefficient KA of the compressor shell under the suction overheat working condition to the environment according to the parameters by the following formula (2):

calculating the heat dissipation Q of the compressor shell under the working conditions of air absorption and liquid carrying to the environment through the following formula (3) according to the parameters_loss：

Q_loss＝KA(T_d-T_air) (3)

Calculating the enthalpy value h of the air suction port of the compressor under the working condition of air suction and liquid through the following formula (4) according to the parameters₁′：

Calculating the actual suction dryness X' of the compressor under the suction liquid-carrying working condition according to the parameters by the following formula (5):

remarking: when X <1, the inspiration is in a liquid state; when X is 1, the inspiration is in a saturated gas state; when X >1, the suction is in an overheated state.

And step S2, adjusting the opening of the electronic expansion valve and the output power of the heater in the calorimetric bucket where the evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range.

The suction dryness is in linear relation with the exhaust temperature and the refrigerant mass flow, and the refrigerant mass flow is in linear relation with the opening of the electronic expansion valve, namely the suction dryness is also in linear relation with the opening of the electronic expansion valve. Therefore, the opening of the electronic expansion valve and the output power of the heater in the calorimetric bucket where the evaporator is located are adjusted according to the actual air suction dryness and the target air suction dryness, and the actual air suction dryness can be accurately adjusted to be within a set range near the target air suction dryness.

In one embodiment, the above-mentioned set range E is a set range of a ratio of an absolute value of a difference between the actual inspiratory quality X' and the target inspiratory quality Xt to the target inspiratory quality Xt.

In one embodiment, the setting range E may be set according to actual conditions, and may be, for example, 0.1% to 2%.

And step S3, testing the performance parameters of the compressor.

Through the above steps S1 and S2, the actual suction dryness of the compressor operation can be adjusted to the set range of the target suction dryness, so that through the step S3, the performance parameters of the compressor can be accurately tested.

In one embodiment, under the target working condition, the suction dryness of the corresponding compressor can be adjusted by adjusting the opening of the electronic expansion valve and the output power Qc of the heater in the calorimetric bucket where the evaporator is located. The opening degree of the electronic expansion valve and the output power Qc of the heater in the calorimetric barrel where the evaporator is positioned are regulated by logic as follows: inputting a target suction dryness Xt, and when the compressor is stably operated to a working condition of suction liquid, obtaining the actual suction dryness X ' of the compressor in the current operation through the formulas (1) to (5), and then calculating the ratio of the absolute value of the suction dryness difference between X ' and Xt to Xt, namely | Xt-X ' |/Xt. If the absolute value Xt-X' |/Xt is less than or equal to E, keeping the opening of the electronic expansion valve and the output power Qc of the heater in the calorimetric bucket where the evaporator is located unchanged until the test is finished; otherwise, the opening degree of the electronic expansion valve and the output power Qc of the heater in the calorimetric barrel where the evaporator is located are adjusted until | Xt-X' |/Xt is less than or equal to E. And when the absolute value Xt-X' |/Xt is less than or equal to E, testing performance parameters of the compressor, such as refrigerating capacity, output power and the like. Therefore, the testing method of the compressor can enable the compressor to stably run to be close to the target suction dryness and test the performance parameters of the compressor.

According to the testing system of the compressor, the actual suction dryness X' can be calculated by obtaining the parameter values in the formulas (1) to (5), and the problem that the conventional testing device cannot identify the suction dryness of the compressor is solved. By the testing method of the compressor, the testing system of the compressor can test the performance parameters of the compressor under the condition of target suction dryness.

In an embodiment, in order to more quickly stabilize to the target dryness of suction Xt, the above method for testing a compressor further includes: calculating the power initial value of the output power of a heater in a calorimetric bucket where an evaporator is located and the flow initial value of the refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated gas enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the condenser outlet enthalpy value; and calculating the opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow. And controlling the opening of the electronic expansion valve to be an opening initial value, and controlling the output power of a heater in the calorimetric bucket where the evaporator is located to be a power initial value.

Since the opening of the electronic expansion valve and the output power of the heater in the heating barrel where the evaporator is located are not necessarily required to be adapted to the test when the compressor is running at the beginning of the test, the corresponding | Xt-X' |/Xt may be greater than E, and therefore the opening of the electronic expansion valve and the output power of the heater in the heating barrel where the evaporator is located need to be adjusted. Through the steps, the power initial value of the output power of the heater in the calorimetric bucket where the evaporator is located and the opening initial value of the opening of the electronic expansion valve are calculated, so that the opening of the electronic expansion valve is controlled to be the opening initial value, the output power of the heater in the calorimetric bucket where the evaporator is located is controlled to be the power initial value, and the opening of the electronic expansion valve and the output power of the heater in the calorimetric bucket where the evaporator is located can be conveniently and quickly adjusted.

In one embodiment, the compressor isentropic efficiency may be calculated based on a target isentropic discharge enthalpy value, a compressor discharge enthalpy value, and a compressor suction enthalpy value. Isentropic efficiency eta of compressors_sAnd the test result is calculated by the following formula (6) according to the working condition that the suction superheat degree is more than or equal to 5 ℃. Wherein, the isentropic exhaust enthalpy value h_2sFor example, the refrigerant may be first passed through the T_sAnd P_sThe parameter library of the corresponding relation table is used for finding the inspiration entropy value S₁Then using the refrigerant and S₁And P_dThe isentropic exhaust enthalpy value h is found out from the parameter library of the corresponding relation table_2s。

Compressor air suction port enthalpy value h₁For example, suction superheat conditions, by taking the refrigerant type and compressor suction temperature T_sPressure P of air suction inlet of compressor_sUsing a refrigerant with T_sAnd P_sH is found out from the parameter library of the corresponding relation table₁。

Enthalpy value h of air outlet of compressor₂For example, the type of refrigerant and the temperature T of the compressor discharge port can be obtained_dPressure P of the compressor discharge port_dUsing a refrigerant with T_dAnd P_dH is found out from the parameter library of the corresponding relation table₂。

Target air suction enthalpy value h_1tAccording to the target suction dryness Xt and the enthalpy value h of the saturated liquid of the evaporator_liqAnd evaporator saturated air enthalpy value h_vapObtained by the following calculation of formula (7).

Target isentropic exhaust enthalpy value h_2tsFor example, the refrigerant may be first passed through the T_sAnd P_sCorresponding relation table ofThe parameter library finds out the target inspiration entropy value S_1tThen using the refrigerant and S_1tAnd P_dThe isentropic exhaust enthalpy value h is found out from the parameter library of the corresponding relation table_2ts。

Initial value h of exhaust enthalpy value₂₀According to the isentropic efficiency eta_sTarget air suction enthalpy value h_1tAnd target isentropic exhaust enthalpy value h_2tsObtained by calculation according to the following formula (8).

Initial power value Q of output power of calorimetric barrel heater₀According to the target suction enthalpy value h_1tEnthalpy value h of outlet of condenser₃Initial value h of exhaust enthalpy value₂₀And the compressor input power P is calculated by the following equation (9). Enthalpy value h of outlet of condenser₃E.g. by taking the refrigerant type and the temperature T at the outlet of the condenser_coPressure P of the compressor discharge port_dUsing a refrigerant with T_coAnd P_dH is found out from the parameter library of the corresponding relation table₃。

Initial value m of refrigerant mass flow₀The initial value Q of the power of the output power of the calorimetric bucket heater can be determined₀Target air suction enthalpy value h_1tEnthalpy value h of outlet of condenser₃Obtained by calculation according to the following formula (10).

The initial value of the opening degree of the electronic expansion valve is based on the initial value m of the mass flow of the refrigerant₀And (6) calculating.

From the above parameters, the compressor isentropic efficiency η is calculated by the following equation (6)_s：

Calculating a target suction enthalpy value h by the following formula (7) based on the above parameters_1t：

h_1t＝h_liq+X_t(h_vap-h_liq) (7)

Based on the above parameters, the initial value h of the exhaust enthalpy value is calculated by the following formula (8)₂₀：

From the above parameters, the power initial value Q of the output power of the thermal bucket heater is calculated by the following formula (9)₀：

Based on the above parameters, the flow rate initial value m of the refrigerant mass flow rate is calculated by the following formula (10)₀：

Calculating the initial power value Q of the output power of the heater in the calorimetric bucket where the evaporator is positioned₀And an initial value m of the refrigerant mass flow₀Then, the output power Qc of the heater in the heating barrel where the evaporator is positioned can be controlled to be the initial power value Q₀The refrigerant mass flow m is an initial flow value m₀(ii) a Even if Qc is Q₀；m＝m₀(ii) a And controlling the opening of the electronic expansion valve to be an opening initial value.

In one embodiment, to more quickly stabilize to the target inspiratory quality Xt, the target exhaust temperature T may be first interpolated_dtThen calculating the opening of the adjusted electronic expansion valve and the output power of a heater in the calorimetric bucket where the evaporator is located; the method is used for iterative calculation until the ratio of the difference value between the target inhalation dryness and the actual inhalation dryness to the target inhalation dryness reaches a set range.

In the above embodiments, referring to fig. 2 and fig. 3, fig. 3 is a specific flowchart of step S2 in the testing method of the compressor according to the embodiment.

In the testing method of the compressor of the embodiment, the step S2 of adjusting the opening of the electronic expansion valve and the output power of the heater in the calorimetric bucket where the evaporator is located according to the actual air quality and the target air quality includes:

s21, calculating an inspiration dryness difference value Xt-X 'between the target inspiration dryness Xt and the actual inspiration dryness X' |;

s22, calculating the absolute value | Xt-X' | of the inspiration dryness difference value and the target inspiration dryness X_tThe ratio of.

Through the above steps S21 and S22, | Xt-X' |/X can be obtained_tAnd comparing the opening of the electronic expansion valve with the set range E conveniently to determine whether the performance parameters of the compressor are suitable for testing when the compressor runs stably under the condition that the opening of the electronic expansion valve and the output power of the heater in the calorimetric bucket where the evaporator is located are adjusted currently.

S23, calculating a target exhaust temperature by an interpolation method according to the difference value of the suction dryness, the two groups of actual suction dryness and the actual exhaust temperature;

and S24, calculating the opening target value of the opening of the adjusted electronic expansion valve and the power target value of the output power of the heater in the heating barrel where the evaporator is located.

Due to the testing system of the compressor, when the compressor is tested, the compressor can be enabled to normally operate, so that the actual suction dryness X' can be obtained through the formula (5), and the actual exhaust temperature T can be obtained through the temperature sensor_d1Let X be₁X', a set of actual inspiratory dryness X is obtained₁With actual exhaust temperature T_d1。

At the initial power value Q of the output power of the calculated heat output barrel heater₀Initial value m of refrigerant mass flow₀Calculating the opening initial value of the opening of the electronic expansion valve, controlling the opening of the electronic expansion valve to be the opening initial value, controlling the output power of a heater in the calorimetric bucket where the evaporator is located to be the power initial value, and obtaining the actual air suction dryness X 'at the moment through the formula (5) after the compressor runs stably so that the actual air suction dryness X' is obtained₂X' and obtaining the actual exhaust temperature T by a temperature sensor_d2Obtaining another set of actual inspiratory dryness X₂With actual exhaust temperature T_d2. Thus, the target exhaust temperature can be calculated by interpolation according to the two groups of data, and then the adjusted electronic expansion valve can be calculatedThe target value of the opening degree and the target value of the output power of the heater in the heating barrel where the evaporator is located.

In the above step, the target exhaust gas temperature T_dtThe calculation can be performed by the following formula (11) by interpolation. Target exhaust enthalpy value h_2tBy refrigerant and target discharge temperature T_dtWith the pressure P of the exhaust_dThe parameter library of the corresponding relation table is searched out. Target capacity thermal bucket heater power Q_tAccording to the target suction enthalpy value h_1tTarget exhaust enthalpy value h_2tEnthalpy value h of outlet of condenser₃And compressor input power P, obtained by calculation from the following equation (12). Target refrigerant mass flow m_tAccording to the target quantity of the heater power Q of the barrel_tTarget air suction enthalpy value h_1tAnd the enthalpy value h of the outlet of the condenser₃And is obtained by calculation of formula (13). Target electronic expansion valve opening according to target refrigerant mass flow m_tAnd (6) calculating.

And S25, controlling the opening of the electronic expansion valve to be adjusted to a target opening value, and controlling the output power of the heater in the heating barrel where the evaporator is located to be adjusted to a target power value.

In step S25, the opening degree of the electronic expansion valve is controlled and adjusted to the target opening degree value, so that the refrigerant mass flow rate m can be equal to the target refrigerant mass flow rate m_tControlling the output power of the heater in the heating barrel where the evaporator is positioned to be adjusted to the power target value, namely Q_c＝Q_t(ii) a The actual suction dryness of the running compressor can be closer to the target suction dryness, and the ratio of the absolute value of the suction dryness difference to the target suction dryness can be more conveniently within a set range so as to be suitable for testing the performance parameters of the compressor.

And S26, acquiring the actual air suction dryness and the actual exhaust temperature of the compressor.

The step S21 of calculating the difference in the quality of inspiration between the target quality of inspiration and the actual quality of inspiration is returned to until the ratio of the absolute value of the difference in the quality of inspiration to the target quality of inspiration is within the set range. That is, steps S21 to S26 are repeated until the ratio of the absolute value of the intake dryness difference to the target intake dryness falls within the set range.

Because the opening degree of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located are adjusted again in the step S25, after the compressor operates stably, a group of actual air suction dryness and actual exhaust temperature can be obtained, namely a third group of actual air suction dryness and actual exhaust temperature can be obtained, then two groups of data with the actual air suction dryness X 'closest to the target air suction dryness Xt are selected, the steps S21 to S26 are repeated, a fourth group of actual air suction dryness and actual exhaust temperature can be obtained, iterative calculation is carried out until | Xt-X' |/Xt is not more than E, adjustment is not carried out again, and performance parameters of the compressor, such as refrigerating capacity, power and the like, are tested.

Based on the above parameters, the target exhaust gas temperature T is calculated by the following equation (11)_dt：

Based on the above parameters, the target caloric cylinder heater power Q is calculated by the following formula (12)_t：

Based on the above parameters, the target refrigerant mass flow rate m is calculated by the following formula (13)_t：

In order to make the testing method of the compressor of the embodiment of the present application more clear to those skilled in the art, the embodiment of the present application provides a more specific flowchart of the testing method of the compressor, as shown in fig. 4, the testing method of the compressor includes:

s101, inputting a compressor model and working conditions (including target suction dryness Xt) of required operation;

s102, judging whether the test type is air-suction and liquid-carrying? If not, executing S116; if so, S102 is performed.

S103, judging whether the machine type has a heat dissipation coefficient KA and an isentropic efficiency eta for the environment_sIs there a If yes, executing S106; if not, S104 is executed.

S104, setting the suction superheat degree of the compressor to be more than or equal to 5 ℃, and testing according to the original suction superheat algorithm.

S105, after the compressor and the compressor testing system are stable, calculating and recording the heat dissipation coefficient KA and the isentropic efficiency eta of the compressor to the environment_sRecording the compressor input power P₁Exhaust temperature T_d1And the like.

In step S105, the heat dissipation coefficient KA and the isentropic efficiency η of the machine type to the environment can be calculated and obtained through the above formula (1), formula (2) and formula (6)_sRecording compressor input power P₁Exhaust temperature T_d1And (4) parameters.

S106, calculating an initial value h of a target exhaust enthalpy value according to set conditions₂₀。

In step S106, the target exhaust enthalpy value initial value h can be calculated by the above-described equations (7) and (8)₂₀。

S107, calculating a power initial value Q of the output power of the thermal bucket heater₀And an initial value m of the refrigerant mass flow₀And make Q_c＝Q₀，m＝m₀。

In this step S107, the power initial value Q of the output power of the thermal bucket heater can be calculated by the above formula (9) and formula (10)₀And an initial value m of the refrigerant mass flow₀。

S108, after the compressor and the testing system of the compressor are stable, and the compressor and the testing system of the compressor are tested according to the actual exhaust temperature T_d2Calculating the heat dissipation Q of the compressor_lossSuction enthalpy value h₁', and recording the compressor input power P₂And exhaust temperature T_d2And the like.

In step S108, the compressor heat dissipation Q_lossIndicates the heat dissipation Q of the current compressor to the environment_loss(ii) a Suction enthalpy value h₁' ZhishiEnthalpy value h of intercurrent inspiration₁'. The heat dissipation Q of the current compressor to the environment can be calculated by the above equation (3)_loss(ii) a Calculating the actual inspiratory enthalpy h by the above equation (4)₁'; recording compressor input power P₂And exhaust temperature T_d2。

And S109, calculating the actual suction dryness X' of the current compressor.

In step S109, the current actual suction dryness X' of the compressor can be calculated by the above equation (5).

S110, judging whether X' <1 is established. If yes, step S114 is performed, and if no, step S111 is performed.

S111, calculating the target exhaust temperature T by using an interpolation formula_dtAnd finding out the corresponding exhaust enthalpy value h_2t。

In step S111, the target exhaust gas temperature T may be calculated by using the above-described interpolation formula (11)_dt。

S112, calculating the output power Q of the target calorifier heater_tRefrigerant mass flow m_t。

In this step S112, the target-calorie tub heater output power Q may be calculated by the above formula (12)_t(ii) a The target refrigerant mass flow m is calculated by the above equation (13)_t。

S113, adjusting the opening of the electronic expansion valve and the output power of the calorimetric barrel heater to enable m to be m_t，Q_c＝Q_tAnd returns to step S108.

In step S113, the opening of the electronic expansion valve is adjusted so that the refrigerant mass flow rate m becomes m_tRegulating output power of heater of heat measuring barrel to make Q_c＝Q_t。

S114, judging whether the absolute value Xt-X' |/Xt is less than or equal to E. If yes, go to step S115; if not, step S111 is performed.

And S115, maintaining and outputting the current working condition control parameters until the test is finished.

In this step S115, the opening degree of the electronic expansion valve and the output Q of the calorimeter vessel heater are maintained_cAnd the parameters are unchanged until the test is finished.

And S116, testing according to the original suction superheat algorithm.

Due to the testing system of the compressor, when the compressor is tested by using the method, the compressor and the testing system are operated firstly, and when the compressor is started to operate, the compressor is overheated for suction, so that the performance parameters of the compressor can be directly tested.

In summary, according to the testing method of the compressor of the embodiment of the present application, the actual air quality of the compressor is obtained, and the opening of the electronic expansion valve and the output power of the heater in the heating tank where the evaporator is located are adjusted according to the actual air quality and the target air quality, so that the actual air quality is within the set range near the target air quality, and the performance parameter of the compressor is tested. Therefore, the testing method of the compressor can enable the compressor to stably run to the target suction dryness and accurately test the performance parameters of the compressor.

It should be understood that, the sequence numbers of the steps in the foregoing embodiments do not imply an execution sequence, and the execution sequence of each process should be determined by its function and inherent logic, and should not constitute any limitation to the implementation process of the embodiments of the present application.

The following are embodiments of a testing apparatus for a compressor disclosed herein, which can be used to perform embodiments of a testing method for a compressor disclosed herein. For the details not disclosed in the embodiments of the testing device for the compressor disclosed in the present application, please refer to the embodiments of the testing method for the compressor disclosed in the present application.

Fig. 5 is a block diagram of a testing apparatus for a compressor according to the present embodiment. As shown in fig. 5, the testing apparatus for a compressor according to the embodiment of the present application includes: an acquisition module 310, an adjustment module 320, and a test module 330. Wherein the content of the first and second substances,

an obtaining module 310, configured to obtain an actual dryness of suction of the compressor;

the adjusting module 320 is used for adjusting the opening of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range;

the testing module 330 is used for testing performance parameters of the compressor.

The testing device of the compressor of the embodiment obtains the actual air suction dryness of the compressor through the obtaining module 310, the adjusting module 320 adjusts the opening of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness, so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is in a set range, and the testing module 330 tests the performance parameters of the compressor to accurately test the performance parameters of the compressor.

In one embodiment, the obtaining module 310 is specifically configured to: and calculating the actual air suction dryness according to the output power of a heater in the calorimetric barrel where the evaporator is positioned, the input power of the compressor, the mass flow of the refrigerant, the heat dissipation capacity of a shell of the compressor to the environment, the exhaust enthalpy value of the compressor, the air suction enthalpy value of the compressor, the outlet enthalpy value of the condenser, the saturated liquid enthalpy value of the evaporator and the saturated gas enthalpy value of the evaporator. Therefore, the actual inspiratory dryness can be accurately calculated.

In one embodiment, referring to fig. 6, the testing apparatus of the compressor further includes a calculating module and a control module, wherein:

the calculating module 340 is used for calculating a power initial value of output power of a heater in a caloric drum where the evaporator is located and a flow initial value of refrigerant mass flow according to the isentropic efficiency of the compressor, the target exhaust pressure, the target suction pressure, the evaporator saturated gas enthalpy value, the target suction dryness, the evaporator saturated liquid enthalpy value and the outlet enthalpy value of the condenser; calculating an opening initial value of the opening of the electronic expansion valve according to the flow initial value of the refrigerant mass flow;

and the control module 350 is configured to control the opening of the electronic expansion valve to be an initial opening value, and control the output power of the heater in the thermal bucket where the evaporator is located to be an initial power value.

Through the setting of calculation module 340 and control module 350, can conveniently adjust the output power of electron expansion valve opening and the interior heater of calorimetric bucket that the evaporimeter is located, and then the operating condition of better control compressor to can make the actual quality of the air intake be located near target quality of the air intake within a set range sooner.

In one embodiment, referring to fig. 7, the adjusting module 320 in the testing apparatus of the compressor according to the embodiment of the present application includes a calculating unit 321, an adjusting unit 322, a controlling unit 323, and a determining unit 324. Wherein:

a calculating unit 321, configured to calculate an inspiratory quality difference between the target inspiratory quality and the actual inspiratory quality, and calculate a ratio between an absolute value of the inspiratory quality difference and the target inspiratory quality;

the adjusting unit 322 is used for calculating a target exhaust temperature by adopting an interpolation method according to the intake dryness difference, the two groups of actual intake dryness and the actual exhaust temperature, and calculating an opening target value of the opening of the adjusted electronic expansion valve and a power target value of the output power of the heater in the calorimetric bucket where the evaporator is located;

a control unit 323 for controlling the opening of the electronic expansion valve to be adjusted to a target opening value, and controlling the output power of the heater in the heating barrel where the evaporator is located to be adjusted to a target power value;

the determination unit 324 is configured to determine whether a ratio of the absolute value of the intake dryness difference to the target intake dryness reaches a set range.

By arranging the calculating unit 321, the adjusting unit 322, the control unit 323 and the judging unit 324 in the adjusting module 320, the target inhalation dryness can be stabilized faster, and the ratio of the difference between the target inhalation dryness and the actual inhalation dryness to the target inhalation dryness can be brought into the set range faster.

In one embodiment, the setting range E may be set according to actual conditions, and may be, for example, 0.1% to 2%.

According to the testing device of the compressor, the actual suction dryness of the compressor is obtained through the obtaining module 310; the adjusting module 320 adjusts the opening of the electronic expansion valve and the output power of the heater in the calorimetric barrel where the evaporator is located according to the actual air suction dryness and the target air suction dryness so that the ratio of the absolute value of the air suction dryness difference between the actual air suction dryness and the target air suction dryness to the target air suction dryness is within a set range; the test module 330 tests performance parameters of the compressor. Therefore, the testing device of the compressor can enable the compressor to stably run to the target suction dryness and accurately test the performance parameters of the compressor.

It should be noted that, for the information interaction, execution process, and other contents between the above-mentioned devices/units, the specific functions and technical effects thereof are based on the same concept as those of the embodiment of the method of the present application, and specific reference may be made to the part of the embodiment of the method, which is not described herein again.

It will be apparent to those skilled in the art that, for convenience and brevity of description, only the above-mentioned division of the functional units and modules is illustrated, and in practical applications, the above-mentioned function distribution may be performed by different functional units and modules according to needs, that is, the internal structure of the apparatus is divided into different functional units or modules to perform all or part of the above-mentioned functions. Each functional unit and module in the embodiments may be integrated in one processing unit, or each unit may exist alone physically, or two or more units are integrated in one unit, and the integrated unit may be implemented in a form of hardware, or in a form of software functional unit. In addition, specific names of the functional units and modules are only for convenience of distinguishing from each other, and are not used for limiting the protection scope of the present application. The specific working processes of the units and modules in the system may refer to the corresponding processes in the foregoing method embodiments, and are not described herein again.

Referring to fig. 8, an embodiment of the present invention further provides a testing apparatus 400 for a compressor, where the testing apparatus 400 for a compressor includes: at least one processor 401, a memory 402 and a computer program 403 stored in the memory 402 and executable on the at least one processor 401, the processor 401 implementing the steps in the test method embodiment of a compressor of any of the embodiments described above when executing the computer program 403.

The Processor 401 may be a Central Processing Unit (CPU), and the Processor 401 may be other general purpose Processor, a Digital Signal Processor (DSP), an Application Specific Integrated Circuit (ASIC), an off-the-shelf Programmable Gate Array (FPGA) or other Programmable logic device, discrete Gate or transistor logic, discrete hardware components, etc. The general purpose processor 401 may be a microprocessor or the processor may be any conventional processor or the like.

The memory 402 may in some embodiments be an internal storage unit of the testing device 400 of the compressor, such as a hard disk or a memory of the testing device 400 of the compressor. The memory 402 may also be an external storage device of the testing device 400 of the compressor in other embodiments, such as a plug-in hard disk, a Smart Media Card (SMC), a Secure Digital (SD) Card, a Flash memory Card (Flash Card), and the like, provided on the testing device 400 of the compressor. Further, the memory 402 may also include both an internal storage unit and an external storage device of the test device 400 of the compressor. The memory 402 is used for storing an operating system, an application program, a BootLoader (BootLoader), data, and other programs, such as program codes of the computer programs. The memory 402 may also be used to temporarily store data that has been output or is to be output.

The embodiment of the present application further provides a computer-readable storage medium, where a computer program is stored, and when the computer program is executed by a processor, the steps in the above-mentioned embodiments of the testing method for the compressors can be implemented.

The integrated unit, if implemented in the form of a software functional unit and sold or used as a stand-alone product, may be stored in a computer readable storage medium. Based on such understanding, all or part of the processes in the methods of the embodiments described above can be implemented by a computer program, which can be stored in a computer-readable storage medium and can implement the steps of the embodiments of the methods described above when the computer program is executed by a processor. Wherein the computer program comprises computer program code, which may be in the form of source code, object code, an executable file or some intermediate form, etc. The computer readable medium may include at least: any entity or device capable of carrying computer program code to a photographing apparatus/terminal apparatus, a recording medium, computer Memory, Read-Only Memory (ROM), Random Access Memory (RAM), an electrical carrier signal, a telecommunications signal, and a software distribution medium. Such as a usb-disk, a removable hard disk, a magnetic or optical disk, etc. In certain jurisdictions, computer-readable media may not be an electrical carrier signal or a telecommunications signal in accordance with legislative and patent practice.

In the above embodiments, the descriptions of the respective embodiments have respective emphasis, and reference may be made to the related descriptions of other embodiments for parts that are not described or illustrated in a certain embodiment.

Those of ordinary skill in the art will appreciate that the various illustrative elements and algorithm steps described in connection with the embodiments disclosed herein may be implemented as electronic hardware or combinations of computer software and electronic hardware. Whether such functionality is implemented as hardware or software depends upon the particular application and design constraints imposed on the implementation. Skilled artisans may implement the described functionality in varying ways for each particular application, but such implementation decisions should not be interpreted as causing a departure from the scope of the present application.

The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.