CN218151325U - Fluid supply system for compressor - Google Patents

Abstract

The present disclosure provides a fluid supply system for a compressor, applied to a refrigeration unit comprising at least a liquid storage device, the fluid supply system for a compressor comprising: a liquid replenishment module that receives liquid refrigerant by gravity of refrigerant liquid in a liquid storage device; and a supply module that receives liquid refrigerant and/or gas refrigerant and/or a liquid-gas refrigerant mixture provided by the liquid replenishment module according to a pressure difference between a pressure of the supply module and the liquid replenishment module; and the supply module provides liquid refrigerant and/or gaseous refrigerant and/or a liquid-gaseous refrigerant mixture to a hydrostatic air bearing used in the compressor; the liquid supplementing module further comprises a first liquid supplementing module and a second liquid supplementing module, and the first liquid supplementing module and the second liquid supplementing module are connected to different liquid storage devices.

Description

Fluid supply system for compressor

Technical Field

The present disclosure relates to a fluid supply system for a compressor.

Background

At present, oil lubrication bearings and suspension bearings are often adopted as bearings of a refrigeration compressor.

Compressors employing oil lubricated bearings require an additional lubrication oil supply system, a lube-refrigerant separation system is required to separate the lube oil entering the refrigerant. After a period of operation, the lubricating oil can be deposited on the inner surfaces of the condenser and the evaporator copper pipes, and the performance of the heat exchanger is reduced. The inner surfaces of copper pipes of the condenser and the evaporator need to be cleaned regularly, and the refrigerant and the lubricating oil need to be replenished regularly. In general, the use of lubricating oil increases the complexity of the system, decreases the reliability and performance of the system, and increases maintenance costs.

The suspension bearing comprises a magnetic suspension bearing and an air suspension bearing, and the air suspension bearing comprises a hydrostatic bearing and a dynamic pressure bearing. Wherein the hydrostatic bearing needs external pressurization, and a gas, liquid or gas-liquid two-phase refrigerant medium is continuously and stably supplied to the hydrostatic bearing through a set of gas/liquid supply system, thereby providing support and lubrication to the rotor. Nevertheless, because the hydrostatic air bearing has high rotation precision, the leakage in the compressor is less, the performance and the service life of the compressor are improved, and the application of the hydrostatic air bearing compressor in the refrigeration industry is concerned.

Storage tank (also known as gas supply tank) the bearing is provided with a lubricating medium, in the refrigeration system, the lubricating medium is the refrigerant circulated by the refrigeration system. Taking the example of the static pressure air bearing exhaust communicating with the evaporator, the bearing pressure difference is the pressure difference between the storage tank and the evaporator. During the start and stop of the unit, the adjustment of working conditions and various running states, the pressure difference of the bearing needs to be kept constant, and only fluctuation in a very small range is allowed. Therefore, the bearing medium has practical value the supply system must have the following features:

1. the storage tank has to be under various working conditions liquid or gaseous refrigerant can be obtained. For example, a unit start may be divided into a cold start and a hot start. When the cold machine is started, the temperatures of the evaporator and the condenser are similar, the position of the refrigerant accumulation is related to the structure of the machine set, the bottoms of the evaporator and the condenser of the horizontal unit are both provided with liquid refrigerant accumulation, and the vertical unit is only provided with liquid refrigerant in the condenser. The temperature of the heat engine state evaporator is obviously lower than that of the condenser, and under the drive of the saturation pressure, whether horizontal or vertical units, the liquid refrigerant is driven to the evaporator. Liquid refrigerant is sometimes present in unit economizers employing two and more stages of compression. Therefore, the bearing air supply system must firstly have the ability to determine the position of the liquid refrigerant and secondly have the ability to deliver the refrigerant to the air supply tank or the storage tank with low power consumption.

2. The bearing fluid supply pressure can vary with the evaporator in time to maintain the requirement of stable bearing differential pressure. If the time lag is long, the pressure fluctuation exceeds the allowable range. One solution is to extend the process of starting and stopping and adjusting the state of the unit, and the disadvantage is that the unit has poor adaptability and is limited in application.

Figure 1 shows a prior art air supply system that takes liquid from the bottom of the evaporator/condenser/economizer, feeds it through a filter and into an air supply tank pressurized by a fuel-free pump, supplies fluid from the air supply tank to the bearings, and connects the bearing exhaust to the evaporator. In order to stabilize the supply pressure, a pressure sensor, a level gauge, and the like are provided in the supply tank in addition to the heater. There are also systems that do not include a supply tank and that provide lubrication medium directly to the bearings from a pump.

The refrigerant pump is a power machine for pressurizing and conveying liquid, only a small amount of gas is allowed to exist at an inlet and an outlet of the refrigerant pump, otherwise, the refrigerant pump is in dry rotation, the liquid cannot enter the refrigerant pump, and finally the refrigerant pump is heated and burnt.

However, in the system shown in fig. 1, gas is present both upstream and downstream of the refrigerant pump. The appearance of gas upstream is summarized as follows: 1. the pipeline loss at the upstream of the pump, the pressure reduction of the saturated liquid and the vaporization of part of the liquid are natural; 2. pressure loss of the filter; 3. the heat exchange between the upstream pipeline and the outside, if the temperature of the liquid in the pipeline is lower than the environment, the environment heats the pipeline to cause the vaporization of the liquid inside. This phenomenon is particularly evident for liquid extraction from the evaporator; 4. the inlet pressure is reduced in the liquid suction process of the refrigerant pump, the refrigerant is vaporized, and the vaporization degree is increased along with the increase of the rotation speed of the refrigerant pump. This phenomenon is also particularly evident for liquid extraction from the evaporator, which requires increased rotational speed to achieve the required head pressure due to low liquid pressure in the evaporator. The condition that gas appears at the downstream is mainly that after the unit stops running for a long time, liquid in the pipeline vaporizes, and the start-up difficulty is caused. It should be noted that the fluid in the piping downstream of the pump is in a super-cooled state after the unit is operated, and the possibility of generating gas is very small.

Therefore, when the liquid needs to be taken from the evaporator, the refrigerant pump cannot work normally due to multiple factors such as environmental heat exchange, filter loss, high pressure head and the like, so that the unit is frequently started and stopped in a heat engine state, and the fault that the refrigerant pump damages the unit and cannot be restarted occurs.

SUMMERY OF THE UTILITY MODEL

In order to solve one of the above technical problems, the present disclosure provides a fluid supply system for a compressor, which is characterized by not including a refrigerant pump and a liquid position sensor.

According to one aspect of the present disclosure, there is provided a fluid supply system for a compressor, applied to a refrigeration unit comprising at least a liquid storage device, the fluid supply system for a compressor comprising:

a liquid replenishment module that receives liquid refrigerant by gravity of refrigerant liquid in a liquid storage device; and

a supply module that receives liquid refrigerant and/or gaseous refrigerant and/or a liquid-gaseous refrigerant mixture provided by a liquid replenishment module according to a pressure difference between a pressure of the supply module and the liquid replenishment module; and the supply module provides liquid refrigerant and/or gaseous refrigerant and/or a liquid-gaseous refrigerant mixture to a hydrostatic gas bearing used in the compressor;

the liquid supplementing module further comprises a first liquid supplementing module and a second liquid supplementing module, and the first liquid supplementing module and the second liquid supplementing module are connected to different liquid storage devices.

According to the fluid supply system for the compressor of at least one embodiment of the present disclosure, a regulating valve is disposed between the fluid replenishing module and the supply module.

According to the fluid supply system for the compressor, the liquid supplementing module comprises a liquid supplementing tank, the liquid supplementing tank is connected to the liquid storage device through a first pipeline, the connection position of the first pipeline and the liquid storage device is located at the lower portion of the liquid storage device, a first switch valve is arranged on the first pipeline, and liquid refrigerant enters the liquid supplementing tank through the first pipeline.

According to the fluid supply system for the compressor in at least one embodiment of the present disclosure, the upper portion of the fluid replacement tank is further connected to the upper portion of the fluid storage device through a second pipeline, wherein the second pipeline is provided with a second switch valve, so that the gas of the fluid replacement tank flows to the fluid storage device through the second pipeline.

According to the fluid supply system for the compressor of at least one embodiment of the present disclosure, the first heating device is disposed in the fluid replenishing tank.

According to the fluid supply system for the compressor of at least one embodiment of this disclosure, the makeup tank is provided with a first pressure sensor.

According to the fluid supply system for the compressor of at least one embodiment of the present disclosure, the supply module includes a supply tank connected to the liquid replenishing module and the static pressure air bearing.

According to the fluid supply system for the compressor of at least one embodiment of this disclosure, the second heating device is arranged in the supply tank.

According to the fluid supply system for a compressor of at least one embodiment of the present disclosure, the supply tank is provided with a second pressure sensor.

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the disclosure and together with the description serve to explain the principles of the disclosure.

Fig. 1 is a schematic configuration diagram of a fluid supply system for a compressor according to an embodiment of the present disclosure.

Fig. 2 is a schematic structural view of a fluid supply system for a compressor according to an embodiment of the present disclosure.

Fig. 3 is a structural schematic view of a fluid supply system for a compressor according to one embodiment of the present disclosure.

FIG. 4 is a schematic illustration of the power consumption for electrical heating per temperature rise of refrigerant in a tank versus the percentage of liquid refrigerant in the tank to the volume of the tank according to one embodiment of the disclosure.

The reference numbers in the figures are in particular:

100 liquid supplementing tank

120 first heating device

140 first pressure sensor

200 first on-off valve: (liquid inlet valve body

300 second switch valve (gas passage)

400 regulating valve

600 supply tank

620 second heating means

640 second pressure sensor

800 filter.

Detailed Description

The present disclosure will be described in further detail with reference to the drawings and embodiments. It is to be understood that the specific embodiments described herein are merely illustrative of the relevant matter and not restrictive of the disclosure. It should be further noted that, for the convenience of description, only the portions relevant to the present disclosure are shown in the drawings.

It should be noted that the embodiments and features of the embodiments in the present disclosure may be combined with each other without conflict. Technical solutions of the present disclosure will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

Unless otherwise indicated, the illustrated exemplary embodiments/examples are to be understood as providing exemplary features of various details of some ways in which the technical concepts of the present disclosure may be practiced. Accordingly, unless otherwise indicated, features of the various embodiments may be additionally combined, separated, interchanged, and/or rearranged without departing from the technical concept of the present disclosure.

The use of cross-hatching and/or shading in the drawings is generally used to clarify the boundaries between adjacent components. As such, unless otherwise specified, the presence or absence of cross-hatching or shading does not convey or indicate any preference or requirement for a particular material, material property, size, proportion, commonality among the illustrated components and/or any other characteristic, attribute, property, etc., of a component. Further, in the drawings, the size and relative sizes of components may be exaggerated for clarity and/or descriptive purposes. While example embodiments may be practiced differently, the specific process sequence may be performed in a different order than that described. For example, two consecutively described processes may be performed substantially simultaneously or in an order reverse to the order described. In addition, like reference numerals denote like parts.

When an element is referred to as being "on" or "over," "connected to" or "coupled to" another element, it can be directly on, connected or coupled to the other element or intervening elements may be present. However, when an element is referred to as being "directly on," "directly connected to" or "directly coupled to" another element, there are no intervening elements present. For purposes of this disclosure, the term "connected" may refer to physically, electrically, etc., and may or may not have intermediate components.

For descriptive purposes, the present disclosure may use methods such as "below 8230; …," "below 8230;" \8230; below 8230; "," below 8230; "," "above 8230" "," "above", "at 8230;", "" above "," higher "and" side (e.g., spatially relative terms, such as "in the sidewalls" and the like, may be used herein to describe one element's relationship to another element(s) as illustrated in the figures. Spatially relative terms are intended to encompass different orientations of the device in use, operation, and/or manufacture in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "below" or "beneath" other elements or features would then be oriented "above" the other elements or features. Thus, the exemplary term "at 8230; \8230;" below "may encompass both an orientation of" above "and" below ". Further, the devices may be otherwise positioned (e.g., rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

The terminology used herein is for the purpose of describing particular embodiments and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. Furthermore, when the terms "comprises" and/or "comprising" and variations thereof are used in this specification, the stated features, integers, steps, operations, elements, components and/or groups thereof are stated to be present but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components and/or groups thereof. It is also noted that, as used herein, the terms "substantially," "about," and other similar terms are used as approximate terms and not as degree terms, and as such, are used to interpret inherent deviations in measured values, calculated values, and/or provided values that would be recognized by one of ordinary skill in the art.

Fig. 2 is a structural schematic view of a fluid supply system for a compressor according to one embodiment of the present disclosure. Fig. 3 is a schematic structural view of a fluid supply system for a compressor according to an embodiment of the present disclosure.

As shown in fig. 2 and 3, the fluid supply system for a compressor provided by the present disclosure may be applied to a refrigerator set.

In an exemplary embodiment, the refrigeration unit includes a compressor unit including an electric motor and a compressor driven by the electric motor, wherein the compressor unit includes hydrostatic air bearings, which may include axial and radial hydrostatic air bearings, and the fluid supply system for the compressor is capable of supplying air to the axial and radial hydrostatic air bearings. The structure of the compressor unit is a structure that is common in the prior art, and is not described in detail here. It will be appreciated by those skilled in the art that the compressor train may be a multi-stage compressor train as is well known in the art, and the structure of the multi-stage compressor train will not be described in detail herein.

The compressor unit is connected to the condenser to cool the high-temperature and high-pressure gas refrigerant output by the compressor unit into liquid refrigerant, that is, the condenser includes liquid refrigerant, and in one embodiment, the liquid refrigerant is located at the middle lower part of the condenser.

The condenser is connected to the evaporator through an expansion valve, the expansion valve is used for decompressing liquid refrigerant in the condenser to generate a mixture of low-temperature and low-pressure gas refrigerant and liquid refrigerant, the liquid refrigerant decompressed by the expansion valve enters the evaporator, the liquid refrigerant is gasified in the evaporator, and the evaporator can absorb a large amount of heat.

The low-temperature low-pressure gas refrigerant generated by the evaporator is delivered to the compressor unit, and is compressed by the compressor unit to generate the high-temperature high-pressure gas refrigerant.

It will be appreciated by those skilled in the art that when the refrigeration unit includes an economizer (flash tank) or the like, the economizer is connected to the condenser and the evaporator.

That is, in the refrigeration unit, liquid refrigerant is in each of the condenser, the evaporator and the economizer, and accordingly, the liquid storage device of the present disclosure includes at least one of the evaporator, the condenser and the economizer.

The fluid supply system for the compressor at least comprises a liquid supplementing module and a supply module.

The liquid supplementing module receives liquid refrigerant through the gravity of refrigerant liquid in the liquid storage device; the supply module receives liquid refrigerant and/or gas refrigerant provided by the liquid supplementing module according to the pressure difference between the pressure of the supply module and the liquid supplementing module; and the supply module provides liquid refrigerant and/or gaseous refrigerant to the hydrostatic air bearing.

In one embodiment, the number of the fluid infusion modules can be one, two, three or the like. When the number of the liquid supplement module is one, the liquid supplement module may be connected to any one of the condenser, the evaporator and the economizer, and preferably, the liquid supplement module is preferentially connected to the condenser in consideration of a high temperature of the liquid refrigerant in the condenser and supplies the liquid refrigerant to the liquid supplement module through the condenser.

In another embodiment, when the number of the liquid replenishing modules is two, the two liquid replenishing modules may be respectively connected to two of the condenser, the evaporator and the economizer; preferably, the two fluid replacement modules can be connected to the condenser and the evaporator, respectively, or to the condenser and the economizer, whereby the condenser, the evaporator and the economizer can supply liquid refrigerant to the fluid replacement modules individually, or simultaneously to different fluid replacement modules.

In a third embodiment, the number of the fluid replacement modules is three, and in this case, three fluid replacement modules are respectively connected to the condenser, the evaporator and the economizer, and accordingly, the condenser, evaporator and economizer may provide liquid refrigerant to the fluid replacement modules individually or simultaneously.

In the present disclosure, a regulating valve 400 is disposed between the fluid infusion module and the supply module; in one embodiment, when the number of the fluid infusion modules is multiple (for example, when the number of the fluid infusion modules is greater than or equal to two), the multiple fluid infusion modules are all connected to the same supply module; of course, those skilled in the art will appreciate that the fluid replacement modules and the supply modules may be arranged in a one-to-one correspondence. Or one liquid supplementing module is connected with a plurality of supply modules. Or a plurality of fluid infusion modules connected to the same supply module.

The structure of the fluid infusion module is explained in detail below.

The liquid supplementing module comprises a liquid supplementing tank 100, the liquid supplementing tank 100 is connected to the liquid storage device through a first pipeline, a first switch valve 200 is arranged on the first pipeline, and liquid refrigerant enters the liquid supplementing tank 100 through the first pipeline. Positionally, the make-up tank 100 is located in a lower portion of the reservoir, such that liquid refrigerant in the reservoir can flow into the make-up tank 100 under the force of gravity.

Preferably, the connection position of the first pipeline and the liquid storage device is positioned at the lower part or the bottom of the liquid storage device, so that the first pipeline can conveniently output liquid refrigerant from the liquid storage device; correspondingly, the connection between the first pipeline and the liquid replenishing tank 100 is arranged at the middle lower part of the liquid replenishing tank 100.

The fluid replenishing tank 100 is further connected to the fluid storage device through a second pipeline, wherein the second pipeline is provided with a second switch valve 300, so that fluid interaction between the fluid storage device and the fluid replenishing tank 100 is realized through the second pipeline. In the present disclosure, the interaction of the gas refrigerant is realized between the liquid storage device and the fluid infusion tank 100 through the second pipeline, so that the gas pressure between the liquid storage device and the fluid infusion tank 100 can be balanced, that is, the flow of the gas in the fluid infusion tank to the fluid infusion device can be realized through the second pipeline. In terms of position, the connection position of the second pipeline and the liquid storage device is positioned at the upper part or the top part of the liquid storage device; correspondingly, the connection of the second pipeline to the fluid reservoir 100 is also located at the upper part/top of said fluid reservoir 100.

In the present disclosure, the liquid replenishing module includes a first heating device 120, and the first heating device 120 is disposed in the liquid replenishing tank 100, so that heat can be provided to the liquid refrigerant in the liquid replenishing tank 100 through the first heating device 120, that is, the liquid refrigerant is heated, and the liquid refrigerant is vaporized to generate a gas refrigerant, thereby increasing the gas pressure in the liquid replenishing tank 100. In a preferred embodiment, the first heating device 120 may be an electric heating device.

More preferably, the liquid replenishing module further comprises a first pressure sensor 140, and the first pressure sensor 140 may be disposed in the liquid replenishing tank 100 and is used for acquiring the pressure of the gas refrigerant in the liquid replenishing tank 100; in the present disclosure, the operation of the fluid supply system for the compressor may be implemented by controlling the first switching valve 200, the second switching valve 300, the regulating valve 400, and the like according to the pressure of the gas refrigerant detected by the first pressure sensor 140.

In a preferred embodiment, the number of the liquid supplementing modules is two, or the liquid supplementing modules include a first liquid supplementing module and a second liquid supplementing module, the first liquid supplementing module is connected with the condenser to receive liquid refrigerant from the condenser, and therefore, the first liquid supplementing module can also be called as a condenser liquid supplementing module; accordingly, a second fluid replacement module is coupled to the evaporator or economizer to receive liquid refrigerant therefrom, and thus may also be referred to as an evaporator fluid replacement module.

The connection between the first fluid infusion module and the condenser and the connection between the second fluid infusion module and the evaporator or the economizer are described in detail above, and are not described in detail herein.

The structure of the supply module is explained in detail below.

The supply module comprises a supply tank 600, the supply tank 600 being connected to a make-up module and a hydrostatic air bearing, e.g. the supply tank 600 being connected to the make-up tank 100, thereby being able to receive liquid refrigerant and/or gaseous refrigerant and/or liquid-gaseous refrigerant mixture from the make-up tank 100. On the other hand, the supply tank 600 is also connected to the hydrostatic air bearings and is capable of supplying liquid refrigerant and/or gaseous refrigerant and/or liquid-gaseous refrigerant mixture to the hydrostatic air bearings so that the hydrostatic air bearings are capable of supporting the rotating shaft by the liquid refrigerant and the gaseous refrigerant. The liquid supplementing module is higher than the supplying module in position.

In the present disclosure, it is considered that the pressure of the liquid refrigerant and/or the gas refrigerant output from the hydrostatic air bearing is low, and the liquid refrigerant and/or the gas refrigerant, mainly the gas refrigerant, is delivered to the evaporator (the inlet of the compressor unit).

In the present disclosure, the supply module includes a second heating device 620, and the second heating device 620 is disposed in the supply tank 600, so that heat can be provided to the liquid refrigerant in the supply tank 600 through the second heating device 620, that is, the liquid refrigerant is heated, and the liquid refrigerant is vaporized to generate a gas refrigerant, thereby increasing the gas pressure in the supply tank 600. In a preferred embodiment, the second heating means 620 may be an electric heating means.

More preferably, the supply module further comprises a second pressure sensor 640, and the second pressure sensor 640 may be disposed at the supply tank 600 for acquiring the pressure of the gas refrigerant in the supply tank 600; in the present disclosure, the operation of the fluid supply system for the compressor may be implemented by controlling the first switching valve 200, the second switching valve 300, the regulating valve 400, and the like according to the pressure of the gas refrigerant detected by the second pressure sensor 640.

In the present disclosure, a drain pipe (not shown) is connected to the supply tank 600, and the drain pipe is provided with a pressure relief valve capable of opening or closing the drain pipe, thereby preventing the pressure of the gas refrigerant in the supply tank 600 from being excessively high, and improving the safety of the fluid supply system for the compressor.

In one embodiment, the drain line may be connected to the evaporator (inlet of the compressor unit) or to the condenser (outlet of the compressor unit)

In the present disclosure, a supply line is disposed between the supply tank 600 and the static pressure air bearing, and a filter 800 is disposed on the supply line to prevent impurities in the liquid refrigerant and the gas refrigerant from damaging the static pressure air bearing and other components.

Through the structural description of the present disclosure, the fluid supply system for a compressor of the present disclosure does not include a pump, or a pump body for conveying liquid refrigerant, thereby effectively solving the technical problem of refrigerant pump damage.

On the other hand, as described by the above-described structure of the present disclosure, the fluid supply system for a compressor of the present disclosure does not include a liquid position sensor, that is, since the first heating device 120 and the first pressure sensor 140, and the second heating device 620 and the second pressure sensor 640 are present in the present disclosure, it is possible to calculate the amounts of liquid refrigerants in the makeup tank 100 and the supply tank 600 through the relationship between the heating time of the heater and the pressure detected by the pressure sensors, thereby avoiding the use of an expensive level gauge, so that the fluid supply system for a compressor is reduced in cost by 80% compared to the related art device, and greatly improves the market competitiveness of the product.

According to another aspect of the present disclosure, there is provided a fluid supply method for a compressor, which includes a fluid replenishing mode and a supply mode; wherein: the supply mode is a process of transferring liquid refrigerant from a liquid storage device into a fluid supply system of the hydrostatic air bearing, and the supply mode is a process of providing liquid refrigerant and/or gas refrigerant to the hydrostatic air bearing.

Preferably, the fluid supply method of the hydrostatic air bearing can be realized by the fluid supply device of the hydrostatic air bearing. The structure of the fluid supply device for the aerostatic bearing is not described in detail herein.

In this disclosure, the fluid infusion mode includes: controlling the second switching valve 300 to make the pressure of the gas refrigerant in the liquid supplementing module and the pressure of the gas refrigerant in the liquid storage device the same; controlling the first switch valve 200 to enable the liquid refrigerant in the liquid storage device to flow to the liquid supplementing module under the action of gravity; controlling the liquid supplementing module to increase the pressure of the gas refrigerant in the liquid supplementing module; and controlling the regulating valve 400 such that the liquid refrigerant and/or the gas refrigerant in the fluid replacement module flows to the supply module.

Accordingly, the provisioning mode includes: the supply module is controlled such that the supply module provides liquid refrigerant and/or gaseous refrigerant to the hydrostatic air bearing.

Specifically, when the fluid replacement is performed, the regulating valve 400 is first closed, that is, the fluid replacement module and the supply module are not communicated with each other.

The second on-off valve 300 is then opened to allow gas communication between the fluid replacement module and the fluid reservoir, e.g., between the fluid replacement tank 100 and the fluid reservoir, at which point the pressure of the gaseous refrigerant in the fluid replacement tank 100 and the fluid reservoir is the same.

Then, the first on-off valve 200 is opened, and at this time, the liquid refrigerant in the liquid storage device flows into the liquid replenishing tank 100 under the action of gravity; and after the set time, the first and second switching valves 200 and 300 are closed.

Then, providing heat to the fluid replacement tank 100, for example, heating the liquid refrigerant in the fluid replacement tank 100, so that part of the liquid refrigerant is vaporized to form a gas refrigerant, and at this time, the gas pressure in the fluid replacement tank 100 will rise; the pressure of the gas refrigerant in the makeup tank 100 is detected by the first pressure sensor 140. When the pressure of the gas refrigerant in the fluid replacement tank 100 is equal to or higher than a set value, the first heating device 120 is turned off.

The regulating valve 400 is opened so that the liquid refrigerant and/or the gas refrigerant in the makeup tank 100 flows into the supply tank 600. In one embodiment, the fluid replenishing tank 100 is communicated with the supply tank 600 through a fluid replenishing pipeline, and the regulating valve 400 is arranged on the fluid replenishing pipeline; furthermore, the connection point of the fluid replacement pipe and the fluid replacement tank 100 is located at the middle-lower part of the fluid replacement tank 100, so that most of or all of the liquid refrigerant in the fluid replacement tank 100 can be forced into the supply tank 600.

That is, the regulating valve 400 maintains a closed state during the time when the liquid refrigerant in the liquid storage device flows to the liquid replenishment module; accordingly, when the regulating valve 400 is opened, the fluid replenishing tank 100 replenishes the supply tank 600; but also the pressure fluctuation of the supply tank 600 can be made within a set range by controlling the opening degree of the regulating valve 400. When the pressure difference (pressure difference) between the fluid replacement tank 100 and the supply tank 600 is reduced to a set value, the regulating valve 400 is closed; the provisioning mode may be performed again.

Accordingly, in the supply tank 600, the pressure of the gas refrigerant in the supply tank 600 may be increased by providing heat to the liquid refrigerant in the supply tank 600, for example, heating the liquid refrigerant by the second heating device 620, and accordingly, the pressure of the gas refrigerant in the supply tank 600 may be detected by the second pressure sensor 640, and when the pressure of the gas refrigerant in the supply tank 600 is greater than or equal to a preset value, the supply tank 600 may provide the liquid refrigerant and/or the gas refrigerant to the aerostatic air bearing.

That is, the regulator valve 400 is preferably in a closed state during the time that the supply tank 600 is providing liquid refrigerant and/or gaseous refrigerant to the hydrostatic air bearing.

According to another important point of the present disclosure, the amount of liquid refrigerant (height of liquid refrigerant or liquid level position of liquid refrigerant) in the makeup tank 100 or the supply tank 600 is obtained by a calculation method in the present disclosure, so that an expensive liquid level meter is not required.

In one embodiment, the volume of liquid refrigerant in the tank can be determined by the relationship between the power consumption of electrical heating per temperature rise of refrigerant in the tank and the percentage of liquid refrigerant in the tank to the volume of the tank; fig. 4 shows the relationship between the electric heating power consumption per temperature rise of the refrigerant in the tank and the percentage of the liquid refrigerant in the tank to the volume of the tank (referred to as power consumption-liquid amount relationship for short).

Specifically, before the fluid supply system for a compressor is used, the time required for the charge tank to be filled with the liquid refrigerant under the action of gravity, the electric heating power consumption per unit temperature rise when the liquid refrigerant is filled in the charge tank, and the electric heating power consumption per unit temperature rise when the liquid refrigerant is filled in the supply tank are measured and recorded in advance, and the content of the liquid refrigerant in the charge tank and/or the supply tank is obtained and controlled based on these measured values.

Correspondingly, if the liquid level of the liquid refrigerant in the liquid supplementing tank 100 is lower than the set value, the liquid supplementing tank 100 is marked as being empty, and the liquid supplementing module is suspended from being used. And when the liquid is replenished next time, the module is replenished, and according to the condition that the liquid level of the liquid refrigerant in the liquid replenishing tank 100 is more than or equal to the set value, the working state of the liquid replenishing module is updated, and the liquid replenishing module is reused.

Similarly, when the liquid level of the liquid refrigerant in all the liquid supplement tanks 100 is lower than the set value, all the liquid supplement tanks 100 are marked as a liquid-free state, and the compressor unit stops working and gives an alarm.

Moreover, when the liquid level of the liquid refrigerant in all the liquid replenishing tanks 100 is equal to or greater than the set value, the liquid replenishing module connected to the condenser is preferentially used to supply the liquid refrigerant and/or the gas refrigerant to the supply module, and at this time, since the saturation pressure of the condenser is higher than that of the evaporator, the power consumption for heating and boosting the pressure is lower.

Similarly, the liquid level gauge is also not provided in the supply tank 600, and the relationship between the power consumption of the electric heating device per temperature rise and the percentage of the liquid refrigerant in the tank body to the volume of the tank body can be obtained by a test method for the supply tank 600, and the liquid level position of the liquid refrigerant in the supply tank 600 can be obtained by a table look-up or a calculation method.

In the present disclosure, the volume of the supply tank 600 is greater than the fluid-replenishing tank 100, that is, the time required for the pressure in the supply tank 600 to fall to the lower limit is greater than the time required for the liquid refrigerant filling process and the heating process of any fluid-replenishing module, thereby enabling the compressor set to operate stably.

In an extreme case, when the pressure of the gas refrigerant in the supply tank 600 is less than a preset value and all the make-up liquid tanks 100 do not reach a liquid state, the second heating device 620 is activated to maintain the pressure in the supply tank 600 for a short time, and the compressor set is stopped and alarmed.

In the preparation stage of starting the refrigerating unit, the liquid supplementing mode is executed at least once, and the amount of the liquid refrigerant in the liquid supplementing tank 100 and/or the supply tank 600 is made to meet the requirement.

When the pressure of the evaporator drops, the pressure differential at the hydrostatic air bearing rises, opening the regulator valve 400 and/or the second on-off valve 300 to allow the liquid refrigerant and/or the gaseous refrigerant in the supply tank 600 to flow to the supply tank 600 to keep the pressure differential at the hydrostatic air bearing constant. On the other hand, the pressure relief valve 700 may be opened to release the pressure so as to keep the pressure difference at the hydrostatic air bearing constant.

When the pressure of the evaporator rises and accordingly the pressure difference at the hydrostatic air bearings is reduced, the first heating device 120 of the liquid supplementing module or the second heating device 620 of the supply module is started to operate, so as to raise the pressure of the liquid supplementing tank 100 and/or the supply tank 600 and keep the pressure difference from the hydrostatic air bearings stable.

Specifically, in the fluid supply method for a compressor of the present disclosure, when the compressor is started (or when the refrigerator set is started), it includes the steps of:

a) Closing the first switch valve 200 of the fluid infusion module, opening the second switch valve 300, closing the regulating valve 400 connecting the fluid infusion module and the supply module pipeline, starting the first heating device (electric heater) in a short time, and determining the content of the liquid refrigerant in the fluid infusion tank according to the relation of power consumption and fluid amount;

b) Starting a second heating device (an electric heater) in a short term, and determining the content of liquid refrigerant in the liquid supply tank according to the relation between power consumption and liquid amount;

c) If the content of the liquid refrigerant of the first liquid supplementing module and the second liquid supplementing module is smaller than a set lower limit, alarming is carried out, and starting of the compressor is forbidden; otherwise, setting a liquid supplementing tank with more liquid refrigerant content as a working tank; if the content of the liquid refrigerant in the working tank exceeds the set upper limit, closing a second switch valve of the working tank after continuously heating to the set temperature, and continuously heating to the set pressure; if the content of the liquid refrigerant in the working tank is lower than the set upper limit, closing a second switch valve of the working tank, and continuously heating to the set pressure;

d) If the content of the liquid refrigerant in the liquid supply tank of the supply module is less than the set lower limit, opening an adjusting valve between the supply tank and the working tank, and conveying the liquid refrigerant to the liquid supply tank; repeating steps a) to d) until the content of the liquid refrigerant in the liquid feed tank reaches a set lower limit;

e) If the content of the liquid refrigerant in the liquid supply tank of the supply module is greater than the set lower limit, the regulating valve is closed, the second heating device (heater) is started to the set pressure, and the compressor is started.

Still further, the fluid supply method for a compressor of the present disclosure further includes: when the compressor is in a normal operation state, supplying the liquid refrigerant to the supply module includes the steps of:

f) Waiting for a liquid taking request of a supply module, and executing the steps g) to j) after receiving the request;

g) For the working tank, starting the electric heater for a short time, and determining the content of the residual liquid refrigerant in the liquid supplementing tank according to the relation between power consumption and liquid amount; obtaining the filling time according to the content of the remaining liquid refrigerant; opening the second switch valve, then opening the first switch valve, closing the first switch valve and the second switch valve after a preset time (less than or equal to full-filling time), starting the electric heater in a short time, and determining the content of the liquid refrigerant in the liquid supplementing tank according to the relation between power consumption and liquid amount;

h) And for the non-working tank, acquiring the filling time according to the liquid content measured last time, opening the first switch valve, or opening the first switch valve and the second switch valve, and closing the first switch valve and the second switch valve after a preset time (less than or equal to the filling time). Starting the electric heater in a short period, and determining the content of the liquid refrigerant in the liquid supplementing tank according to the relation of power consumption and liquid amount;

i) If the contents of the liquid refrigerants of the condenser liquid replenishing module and the evaporator liquid replenishing module are both smaller than a set lower limit, alarming is carried out, and the compressor is forced to stop; otherwise, setting the liquid replenishing tank with more liquid refrigerant content as a working tank. And if the content of the liquid in the working tank exceeds the set upper limit, opening the second switch valve, continuously heating to the set temperature, closing the second switch valve of the working tank, and continuously heating to the set pressure. And if the content of the liquid in the working tank is lower than the set upper limit, closing a second switch valve of the working tank, and continuously heating to the set pressure. Opening a second switch valve of the non-working tank;

j) Opening a regulating valve between the liquid supply tank and the working tank, and conveying liquid refrigerant to the liquid supply tank; when the pressures of the working tank and the liquid supply tank are balanced, the regulating valve is closed.

In a specific embodiment, when the pressure of the liquid supply tank is lower than the set lower limit, the electric heater is started to lift the pressure in the tank, and the content of liquid refrigerant in the tank is calculated; when the content of the liquid refrigerant in the tank is lower than the set lower limit, a liquid taking request is sent.

In a preferred embodiment, when the pressure in the feed tank exceeds a set upper limit, a regulating valve between the feed tank and the non-working tank is opened to reduce the pressure of the feed tank.

In the description herein, reference to the description of the terms "one embodiment/mode," "some embodiments/modes," "example," "specific example," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment/mode or example is included in at least one embodiment/mode or example of the application. In this specification, the schematic representations of the terms used above are not necessarily intended to be the same embodiment/mode or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments/modes or examples. Furthermore, the various embodiments/modes or examples and features of the various embodiments/modes or examples described in this specification can be combined and combined by one skilled in the art without being mutually inconsistent.

Furthermore, 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 at least one of the feature. In the description of the present application, "plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

It will be understood by those skilled in the art that the foregoing embodiments are provided merely for clarity of explanation and are not intended to limit the scope of the disclosure. Other variations or modifications may occur to those skilled in the art, based on the foregoing disclosure, and are still within the scope of the present disclosure.

Claims (9)

1. A fluid supply system for a compressor applied to a refrigeration unit comprising at least a liquid storage device, characterized in that it comprises:

a liquid replenishment module that receives liquid refrigerant by gravity of refrigerant liquid in a liquid storage device; and

a supply module that receives liquid refrigerant and/or gaseous refrigerant and/or a liquid-gaseous refrigerant mixture provided by a liquid replenishment module according to a pressure difference between a pressure of the supply module and the liquid replenishment module; and the supply module provides liquid refrigerant and/or gaseous refrigerant and/or a liquid-gaseous refrigerant mixture to a hydrostatic gas bearing used in the compressor;

the liquid supplementing module further comprises a first liquid supplementing module and a second liquid supplementing module, and the first liquid supplementing module and the second liquid supplementing module are connected to different liquid storage devices.

2. The fluid supply system for a compressor according to claim 1, wherein a regulating valve is disposed between the fluid replacement module and the supply module.

3. The fluid supply system for a compressor according to claim 1, wherein the fluid replenishing module comprises a fluid replenishing tank connected to the fluid storage device through a first pipeline, a connection point of the first pipeline and the fluid storage device is located at a lower portion of the fluid storage device, wherein a first on-off valve is arranged on the first pipeline, and liquid refrigerant enters the fluid replenishing tank through the first pipeline.

4. A fluid supply system for a compressor as set forth in claim 3 wherein said charge tank upper portion is further connected to said reservoir upper portion by a second line, wherein said second line is provided with a second on/off valve for effecting flow of charge tank gas to the reservoir through the second line.

5. The fluid supply system for a compressor according to claim 3, wherein a first heating means is provided in the fluid replenishment tank.

6. The fluid supply system for a compressor as set forth in claim 5, wherein said makeup tank is provided with a first pressure sensor.

7. The fluid supply system for a compressor as set forth in claim 1, wherein the supply module includes a supply tank connected to the fluid replacement module and the hydrostatic air bearing.

8. The fluid supply system for a compressor of claim 7 wherein a second heating device is disposed within the supply tank.

9. The fluid supply system for a compressor of claim 8 wherein the supply tank is provided with a second pressure sensor.

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