CN114198944A

CN114198944A - Compressor and liquid supply system of compressor

Info

Publication number: CN114198944A
Application number: CN202111385094.5A
Authority: CN
Inventors: 杨明威; 张晓锐; 张捷; 陶祥先; 毛守博
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Priority date: 2021-11-22
Filing date: 2021-11-22
Publication date: 2022-03-18
Anticipated expiration: 2041-11-22
Also published as: WO2023087710A1; CN114198944B

Abstract

The application relates to the technical field of refrigeration equipment and discloses a compressor. The method comprises the following steps: the cooling device comprises a shell, a liquid inlet and a liquid outlet, wherein the shell is used for limiting a containing cavity, a cooling pipeline and an air supply pipeline which are arranged in parallel; the motor is positioned in the accommodating cavity and is communicated with the liquid inlet through the cooling pipeline, and liquid refrigerant enters the cooling pipeline through the liquid inlet to cool the motor; and the bearing is positioned in the accommodating cavity and communicated with the liquid inlet through the air supply pipeline, and a liquid refrigerant enters the air supply pipeline through the liquid inlet and is changed from a liquid state to a gas state in the air supply pipeline so as to suspend the bearing. The compressor in this embodiment can guarantee the refrigerant that gets into the bearing to guarantee the stability of bearing air feed. The application also discloses a liquid supply system of the compressor.

Description

Compressor and liquid supply system of compressor

Technical Field

The application relates to the technical field of refrigeration equipment, for example to a compressor and a liquid supply system of the compressor.

Background

At present, in a high-speed type compressor, a rotor of the compressor rotates at a high speed during operation, and a reliable bearing is required to support the rotor. The bearings used by the conventional compressor rotor mainly comprise a rolling bearing, an oil film bearing and a magnetic suspension bearing. In the related art, there are compressors that use air bearing to support rotation of a rotor. The compressor adopting the gas suspension bearing mainly uses gas to support the rotor, and the working principle is that a gas film is automatically formed between the gas suspension bearing and the rotor to support the rotor in the high-speed rotation process of the rotor.

The prior art discloses a compressor, which comprises a cylinder body, a bearing and a bearing seat, wherein the cylinder body comprises a mounting cavity; the stator is fixedly arranged in the mounting cavity and comprises a rotor mounting hole; the rotor is rotatably arranged in the rotor mounting hole; the air suspension thrust bearing is used for bearing the axial force of the rotor; the separation structure is fixedly arranged in the installation cavity and divides the installation cavity into a motor cavity for installing the stator and a bearing cavity for installing the air suspension thrust bearing, and the bottom of the separation structure and/or the barrel is/are provided with a communication structure which is communicated with the motor cavity and the bearing cavity so as to introduce liquid cooling fluid at the bottom of the motor cavity into the bearing cavity; and the bearing cavity liquid level adjusting device comprises a cooling fluid bypass structure which is communicated with the outside of the compressor and a sensing device which is coupled with the cooling fluid bypass structure, wherein the sensing device is used for detecting the state information of the cooling fluid in the bearing cavity and controlling the cooling fluid bypass structure to be opened or closed according to the state information.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

after the liquid refrigerant needs to cool the stator, the liquid refrigerant is continuously vaporized to absorb heat and then provides gas for the bearing. The supply of the bearing gas is limited by factors such as the temperature and the structure of the motor, so that the bearing gas supply of the compressor is unstable.

Disclosure of Invention

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a compressor and a liquid supply system of the compressor, so as to improve the stability of air supply of a bearing of the compressor.

The disclosed embodiment provides a compressor, which includes: the cooling device comprises a shell, a liquid inlet and a liquid outlet, wherein the shell is used for limiting a containing cavity, a cooling pipeline and an air supply pipeline which are arranged in parallel; the motor is positioned in the accommodating cavity and is communicated with the liquid inlet through the cooling pipeline, and liquid refrigerant enters the cooling pipeline through the liquid inlet to cool the motor; and the bearing is positioned in the accommodating cavity and communicated with the liquid inlet through the air supply pipeline, and a liquid refrigerant enters the air supply pipeline through the liquid inlet and is changed from a liquid state to a gas state in the air supply pipeline so as to suspend the bearing.

The embodiment of the present disclosure also discloses a liquid supply system of a compressor, including: a compressor as described in any of the above embodiments; and the main refrigerant loop is provided with a liquid taking port, and the liquid taking port is communicated with the liquid inlet through a liquid taking pipeline.

The compressor and the liquid supply system of the compressor provided by the embodiment of the disclosure can realize the following technical effects:

after entering the compressor from the liquid inlet, the liquid refrigerant can flow into the cooling pipeline and the air supply pipeline simultaneously. The refrigerant required by the air supply pipeline can be directly obtained from the outside through the air supply pipeline, and the gaseous refrigerant generated after the motor is cooled by the liquid refrigerant only depending on the cooling pipeline is not needed. The compressor in this embodiment can guarantee the volume of the refrigerant that gets into the bearing to guarantee the stability of bearing air feed.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

FIG. 1 is a schematic diagram of a compressor feed system according to an embodiment of the present disclosure;

FIG. 2 is a schematic diagram of another compressor liquid supply system provided by an embodiment of the present disclosure;

FIG. 3 is a schematic diagram of another compressor liquid supply system provided by an embodiment of the present disclosure;

FIG. 4 is a schematic diagram illustrating a liquid supply system of another compressor provided by an embodiment of the present disclosure;

FIG. 5 is a schematic cross-sectional view of the interior of a compressor provided by an embodiment of the present disclosure;

FIG. 6 is an enlarged schematic view of portion A of FIG. 5;

FIG. 7 is a schematic diagram of a control method for a compressor according to an embodiment of the present disclosure;

FIG. 8 is a schematic diagram of another control method for a compressor provided by an embodiment of the present disclosure;

FIG. 9 is a schematic diagram of a control method for a liquid supply system of a compressor according to an embodiment of the present disclosure;

FIG. 10 is a schematic diagram of another control method for a liquid supply system of a compressor provided in accordance with an embodiment of the present disclosure;

FIG. 11 is a schematic diagram of another control method for a liquid supply system of a compressor provided in accordance with an embodiment of the present disclosure;

FIG. 12 is a schematic diagram of another control method for a liquid supply system of a compressor provided in accordance with an embodiment of the present disclosure;

FIG. 13 is a schematic view of a mating structure of a first blade and a rotor provided by embodiments of the present disclosure;

FIG. 14 is a schematic view of a second bucket and rotor mating configuration provided by embodiments of the present disclosure.

Reference numerals:

10. a compressor; 101. a bearing; 1011. a first bearing; 1012. a second bearing; 102. a motor; 1021. a stator; 1022. a rotor; 103. a gas supply line; 1031. a first air supply line; 1032. a second gas supply line; 104. a cooling pipeline; 105. a throttling device; 1051. a second throttling device; 1052. a third throttling means; 106. a first regulating valve; 1061. a first sub-regulator valve; 1062. a second sub-regulator valve; 107. a second regulating valve; 108. a housing; 1081. an accommodating chamber; 1082. a motor cavity; 1083. a second detection device; 109. a gas return line; 110. a liquid inlet; 111. a spiral cooling flow channel; 20. a condenser; 201. a liquid sac; 30. a liquid taking pipeline; 301. a first liquid extraction pipeline; 3011. a first solenoid valve; 302. a second liquid taking pipeline; 3021. a second solenoid valve; 3022. a pressurizing device; 303. a filter; 304. a pressure regulating valve; 305. a check valve; 306. a fifth detecting device; 40. an evaporator; 50. a first throttling device; 60. a refrigerant pipeline; 701. an exhaust line; 801. a first blade; 802. a second blade.

Detailed Description

So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their examples and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more unless otherwise specified.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. For example, a and/or B, represents: a or B, or A and B.

It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

As shown in fig. 1 to 4, the present disclosure provides a liquid supply system of a compressor, which includes a main refrigerant circuit including a compressor 10, a condenser 20, a first throttling device 50 and an evaporator 40, which are communicated with each other through a refrigerant pipeline 60. The refrigerant pipeline 60 includes a first refrigerant pipeline, a second refrigerant pipeline and a third refrigerant pipeline.

The evaporator 40 transmits the low-temperature and low-pressure gaseous refrigerant to the compressor 10 through the first refrigerant pipeline, the compressor 10 compresses the low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant, and then transmits the high-temperature and high-pressure gaseous refrigerant to the condenser 20 through the second refrigerant pipeline 60. The high-temperature and high-pressure gaseous refrigerant is cooled in the condenser 20 to become a normal-temperature and high-pressure liquid refrigerant.

The normal-temperature high-pressure liquid refrigerant passes through the third refrigerant pipeline and the first throttling device 50 and then returns to the evaporator 40 again. After the liquid refrigerant at normal temperature and high pressure reaches the evaporator 40 from the first throttling device 50, the space is suddenly increased, the pressure is reduced, and the liquid refrigerant is changed into the liquid refrigerant at low temperature and low pressure. The low-temperature low-pressure liquid refrigerant is vaporized in the evaporator 40 to become a low-temperature low-pressure gaseous refrigerant. Then, the evaporator 40 transfers the low-temperature and low-pressure gaseous refrigerant to the compressor 10 through the first refrigerant pipe again, thereby completing the refrigeration cycle.

The arrows in fig. 1 to 4 indicate the flow direction of the refrigerant in the liquid supply system of the compressor.

The compressor 10 includes a bearing 101 and a motor 102, the motor 102 includes a stator 1021 and a rotor 1022, and the bearing 101 is supported above the rotor 1022 to support the rotor 1022 for rotation.

Alternatively, the compressor 10 includes, but is not limited to, an air-suspension compressor, a gas-liquid mixed bearing press, a compressor with a gas refrigerant or a liquid refrigerant lifting shaft, and the like.

As shown in fig. 5 and 6, embodiments of the present disclosure provide a compressor 10, the compressor 10 including a housing 108, a motor 102, and a bearing 101. The shell 108 defines a cooling pipeline 104 and an air supply pipeline 103 which are arranged in parallel, and the shell 108 is provided with an inlet 110; the motor 102 is positioned in the accommodating cavity 1081 and is communicated with the liquid inlet 110 through the cooling pipeline 104, and the liquid refrigerant enters the cooling pipeline 104 through the liquid inlet 110 to cool the motor 102; the bearing 101 is located in the accommodating cavity 1081 and is communicated with the liquid inlet 110 through the gas supply pipeline 103, and the liquid refrigerant enters the gas supply pipeline 103 through the liquid inlet 110 and changes from a liquid state to a gas state in the gas supply pipeline 103 to suspend the bearing 101.

In fig. 5 and 6, arrows indicate the flow direction of the refrigerant inside the compressor.

By adopting the compressor 10 of the embodiment, the cooling pipeline 104 and the air supply pipeline 103 can both feed liquid refrigerant from the liquid inlet 110, and the gaseous refrigerant of the air supply pipeline 103 can be directly obtained from the outside through the air supply pipeline 103, so that the gaseous refrigerant generated after the motor 102 is cooled by the liquid refrigerant only depending on the cooling pipeline 104 is not needed, and the gas entering the bearing 101 can be further ensured, thereby ensuring the stability of the air supply of the bearing 101.

Optionally, the number of the liquid inlets 110 may be multiple, and the multiple liquid inlets 110 include a first liquid inlet and a second liquid inlet, the first liquid inlet is communicated with the air supply pipeline 103, and the second liquid inlet is communicated with the cooling pipeline 104.

In this embodiment, the cooling pipeline 104 and the air supply pipeline 103 are independent from each other and do not interfere with each other, and the pressure of the liquid refrigerant of the air supply pipeline 103 and the flow rate of the liquid refrigerant of the cooling pipeline 104 can be independently adjusted. Not only can ensure the gaseous refrigerant required by the suspension bearing 101, but also can sufficiently cool the motor 102, thereby ensuring the reliable operation of the compressor 10.

Optionally, when the number of the liquid inlets 110 is one, both the cooling pipeline 104 and the gas supply pipeline 103 are communicated with the liquid inlets 110, wherein after the liquid refrigerant flows into the liquid inlets 110, a part of the liquid refrigerant enters the cooling pipeline 104 for cooling the motor 102, and the other part of the liquid refrigerant enters the gas supply pipeline 103 and changes from a liquid state to a gas state in the gas supply pipeline 103 to suspend the bearing 101.

With the compressor 10 of the present embodiment, after the liquid refrigerant passes through the liquid inlet 110, a portion of the liquid refrigerant enters the cooling pipeline 104 for cooling the motor 102, so as to ensure the normal operation of the motor 102 of the compressor 10. Another part of the liquid refrigerant enters the air supply pipe 103 and changes from liquid to gas in the air supply pipe 103 to suspend the bearing 101. The compressor 10 of the embodiment of the present disclosure utilizes the liquid inlet 110 to feed liquid, which can simultaneously satisfy the suspension bearing 101 and the cooling compressor 10, thereby facilitating the connection of the external liquid-taking pipeline 30 and the installation of the compressor 10.

Optionally, the compressor 10 further includes a throttling device 105, and the throttling device 105 is disposed in the gas supply line 103 and is configured to change the liquid refrigerant of the gas supply line 103 into a gaseous refrigerant.

In the embodiment of the present disclosure, the liquid refrigerant in the air supply pipe 103 is throttled by the throttling device 105 and then changed into the gaseous refrigerant, and the gaseous refrigerant is supplied to the bearing 101, so that the bearing 101 is suspended. By providing the throttle device 105 in the air supply line 103, a heating device or the like can be omitted, and the energy consumption of the compressor 10 can be reduced.

Alternatively, the throttling device 105 comprises a micro-orifice, a capillary throttling device, or the like.

The principle of throttling by the throttling device 105 is as follows: the liquid refrigerant will form a local constriction at the restriction 105, thereby increasing the flow rate of the liquid refrigerant and decreasing the static pressure, thus creating a static pressure differential across the restriction 105. Thereby gradually depressurizing the liquid refrigerant into a gaseous refrigerant, which can suspend the bearing 101.

In practical applications, since the bearing 101 may generate heat during operation of the compressor 10, the liquid refrigerant of the air supply line 103 may also directly flow to the bearing 101, the liquid refrigerant can exchange heat with the bearing 101, and the liquid refrigerant is changed into a gaseous refrigerant after heat exchange. With the arrangement, air can be supplied to the bearing 101, the bearing 101 can be cooled, and the normal operation of the bearing 101 and the reliable movement of the compressor 10 are ensured.

In some cases, the liquid refrigerant may be changed into a gas-liquid mixed mist refrigerant after passing through the throttling device 105, and the mist refrigerant may not only support the suspension bearing 101 but also cool the bearing 101.

Optionally, the compressor 10 further includes a communication pipeline, and the communication pipeline communicates the cooling pipeline 104 and the air supply pipeline 103, so that the gaseous refrigerant after heat exchange with the motor 102 flows to the bearing 101 to suspend the bearing 101.

After the liquid refrigerant in the cooling pipeline 104 cools the motor 102 and absorbs heat of the motor 102, the liquid refrigerant is gasified into a gaseous refrigerant, and the pressure in the cooling pipeline 104 is increased. The gaseous refrigerant enters the air supply pipeline 103 through the communication pipeline, so that the pressure in the cooling pipeline 104 can be reduced, and the liquid refrigerant can normally circulate. On the other hand, the gas refrigerant is supplied to the air supply line 103 through the communication line, and the air pressure in the air supply line 103 is increased, so that the bearing 101 is suspended, and the compressor 10 operates normally.

By adopting the optional embodiment, the refrigerant can be more reasonably utilized, the utilization rate of the gaseous refrigerant is improved, the operation energy consumption of the compressor 10 is reduced, and the use cost is reduced.

Optionally, the compressor 10 further includes an ejector, the ejector is disposed in the air supply pipeline 103, and the communicating pipeline is communicated with the air supply pipeline 103 through the ejector.

The communicating pipeline is communicated with the air supply pipeline 103 through an ejector, and in the ejector, the gaseous refrigerant provided by the communicating pipeline 130 ejects the liquid refrigerant in the air supply pipeline 103, so that the liquid refrigerant in the air supply pipeline 103 is changed into a high-pressure gas-liquid two-phase refrigerant. The high-pressure gas-liquid two-phase refrigerant is supplied to the bearing 101 to suspend the bearing 101, so that the compressor 10 operates normally.

Optionally, the injection device and the throttling device 105 are arranged in sequence along the flow direction of the cooling medium in the air supply pipeline 103.

Optionally, the compressor 10 further comprises a pressure adjusting device, which is disposed in the air supply line 103 and is used for adjusting the pressure of the air supply line.

In the embodiment of the present disclosure, the pressure adjusting device may adjust the pressure of the liquid refrigerant in the air supply line 103 to ensure that the pressure of the liquid refrigerant flowing to the throttling device 105 meets the requirement, so that the pressure of the refrigerant throttled by the throttling device 105 meets the pressure of the suspension of the bearing 101.

Optionally, the pressure adjusting device includes a first adjusting valve 106, the first adjusting valve 106 is disposed on the gas supply line 103, and the first adjusting valve 106 can adjust a flow rate of a liquid refrigerant of the gas supply line 103 to adjust a pressure of the gas supply line.

In this embodiment, the air supply pipe 103 is defined by the shell 108 of the compressor 10, so the pipe area of the air supply pipe 103 is fixed, and the first regulating valve 106 can regulate the flow rate of the liquid refrigerant of the air supply pipe 103, wherein the flow rate of the liquid refrigerant is increased, the flow speed is also increased, and the pressure of the liquid refrigerant is also increased. Similarly, the flow rate of the liquid refrigerant is reduced, the flow speed is also reduced, and the pressure of the liquid refrigerant is also reduced.

Optionally, as shown in fig. 6, the compressor 10 further includes a second regulating valve 107, a first detecting device and a controller; the second regulating valve 107 is arranged on the cooling pipeline 104 and is used for regulating the flow of the liquid refrigerant of the cooling pipeline 104; the first detecting device is disposed in the air supply line 103 to detect a pressure of the air supply line.

Alternatively, in the case that the number of the liquid inlets 110 is one, the controller is connected to the first regulating valve 106, the first regulating valve 106 and the first detecting device, and the controller is capable of receiving the pressure of the gas supply line and adjusting the opening degree of the first regulating valve 106 and the opening degree of the second regulating valve 107 according to the pressure of the gas supply line.

In this embodiment, under the condition that the amount of the liquid refrigerant flowing through the liquid inlet 110 is not changed, the pressure of the air supply pipeline 103 and the pressure of the cooling pipeline 104 are adjusted by the first adjusting valve 106 and the second adjusting valve 107, so as to adjust the pressure of the refrigerant flowing to the bearing 101, and ensure that the pressure of the refrigerant flowing to the bearing 101 can suspend the bearing 101.

The first detection device is a pressure sensor.

As shown in fig. 7, an embodiment of the present disclosure provides a control method for a compressor 10, including:

s701, the controller acquires the pressure of the air supply pipeline.

S702, the controller adjusts the opening degree of the first adjusting valve 106 and the opening degree of the second adjusting valve 107 according to the pressure of the air supply pipeline.

In this embodiment, under the condition that the amount of the liquid refrigerant flowing through the liquid inlet 110 is not changed, the pressure of the air supply pipeline 103 and the pressure of the cooling pipeline 104 are adjusted by the first adjusting valve 106 and the second adjusting valve 107, so as to adjust the pressure of the refrigerant flowing to the bearing 101, and to ensure that the pressure of the refrigerant flowing to the bearing 101 can suspend the bearing 101.

Alternatively, in the case where the pressure of the gas supply line is less than the first preset pressure, the controller controls the second regulating valve 107 to decrease the opening degree, and controls the first regulating valve 106 to increase the opening degree to increase the pressure of the gas supply line.

In this embodiment, when the pressure of the liquid refrigerant in the air supply line 103 is smaller than the first preset pressure, the pressure of the refrigerant flowing to the bearing 101 is smaller, which is insufficient to suspend the bearing 101, so that the opening of the second regulating valve 107 is controlled to decrease, and the refrigerant flow of the cooling line 104 is decreased. Meanwhile, the first regulating valve 106 is controlled to increase the opening degree and increase the flow rate of the air supply pipeline 103, so as to increase the pressure of the refrigerant of the air supply pipeline 103, and ensure that the pressure of the refrigerant flowing to the bearing 101 can suspend the bearing 101.

Alternatively, in the case where the pressure of the gas supply line is greater than the second preset pressure, the controller controls the second regulating valve 107 to increase the opening degree, and controls the first regulating valve 106 to decrease the opening degree to decrease the pressure of the gas supply line.

In this embodiment, when the air supply line 103 is higher than the second preset pressure, the pressure of the liquid refrigerant in the air supply line 103 is higher, which may cause the pressure of the refrigerant flowing to the bearing 101 to be higher, and damage the bearing 101. Therefore, the second regulating valve 107 is controlled to increase the opening degree, thereby increasing the refrigerant flow rate of the cooling line 104. Meanwhile, the first regulating valve 106 is controlled to reduce the opening degree and the flow of the air supply pipeline 103, so that the pressure of the refrigerant of the air supply pipeline 103 is reduced, the pressure of the refrigerant flowing to the bearing 101 is ensured to suspend the bearing 101, and the bearing 101 cannot be damaged.

Alternatively, the first regulating valve 106 is a solenoid valve, a pressure regulating valve, or the like, and the second regulating valve 107 is a solenoid valve, or the like.

Alternatively, in the case where the pressure of the gas supply line is greater than or equal to the first preset pressure and less than or equal to the second preset pressure, the controller controls the first regulating valve 106 to maintain the opening degree to maintain the pressure of the gas supply line; wherein the first preset pressure is smaller than the second preset pressure.

In this embodiment, when the pressure of the air supply line is greater than or equal to the first preset pressure and less than or equal to the second preset pressure, the pressure of the liquid refrigerant in the air supply line 103 flowing to the bearing 101 is within the pressure range required by the bearing 101, so that the bearing 101 can be suspended without damaging the bearing 101. The controller controls the pressure regulating valve 304 to maintain the opening degree to maintain the refrigerant pressure of the air supply line 103.

Alternatively, the first preset pressure may be a minimum critical value of the pressure required by the bearing 101, and the second preset pressure may be a maximum critical value of the pressure required by the bearing 101. The minimum limit value of the pressure required by the bearing 101 is a third preset pressure, and the maximum limit value of the pressure required by the bearing 101 is a fourth preset pressure. The third preset pressure is smaller than the first preset pressure, and the fourth preset pressure is larger than the second preset pressure.

In this embodiment, considering that it takes time for the liquid refrigerant of the air supply line 103 to flow to the bearing 101 after adjusting the pressure, especially at the start-up stage of the compressor 10, the bearing 101 does not have the gaseous refrigerant, so as to avoid the pressure of the gaseous refrigerant at the bearing 101 being insufficient, the third preset pressure is smaller than the first preset pressure, so as to ensure that the bearing 101 is not damaged in the process of flowing the adjusted liquid refrigerant to the bearing 101. Similarly, in order to avoid the pressure of the gaseous refrigerant at the bearing 101 from being too high, when the pressure of the air supply line reaches a second preset pressure, the controller timely adjusts the pressure of the liquid refrigerant of the air supply line 103 to be small, so as to avoid the bearing 101 from being at the maximum limit value of the required pressure, and thus damage to the bearing 101 is caused.

Referring to fig. 8, another control method for the compressor 10 is further provided in an embodiment of the present disclosure, including:

s801, acquiring the pressure of the air supply pipeline by the controller.

S802, the controller judges whether the pressure of the air supply pipeline is larger than or equal to a first preset pressure.

S803, in the case that the pressure of the gas supply line is less than the first preset pressure, the controller controls the second regulating valve 107 to decrease the opening degree, and controls the first regulating valve 106 to increase the opening degree to increase the pressure of the gas supply line.

S804, under the condition that the pressure of the air supply pipeline is smaller than or equal to the first preset pressure, the controller judges whether the pressure of the air supply pipeline is smaller than or equal to the second preset pressure.

S805, in the case that the pressure of the gas supply line is greater than the second preset pressure, the controller controls the second regulating valve 107 to increase the opening degree, and controls the first regulating valve 106 to decrease the opening degree to decrease the pressure of the gas supply line.

S806, under the condition that the pressure of the air supply pipeline is greater than or equal to a first preset pressure and less than or equal to a second preset pressure, the controller controls the first regulating valve 106 to keep the opening degree so as to keep the pressure of the air supply pipeline; wherein the first preset pressure is smaller than the second preset pressure.

In this embodiment, the pressure of the liquid refrigerant in the air supply line 103 after flowing to the bearing 101 can be within the pressure range required by the bearing 101, so that the bearing 101 can be suspended without damaging the bearing 101.

Optionally, the accommodating cavity 1081 includes a motor cavity 1082, the motor 102 is located in the motor cavity 1082, and the compressor 10 further includes a second detecting device 1083, where the second detecting device 1083 is located in the motor cavity 1082, and is configured to detect a temperature of the motor cavity 1082; the controller is connected to a second sensing device 1083, the controller capable of receiving the temperature of the motor cavity 1082.

In this embodiment, the motor 102 is located in the motor cavity 1082, the motor 102 includes a stator 1021 and a rotor 1022, the rotor 1022 is installed in the stator 1021 and can rotate relative to the stator 1021, and during the rotation of the rotor 1022, both the stator 1021 and the rotor 1022 generate heat, which in turn can cause the temperature of the motor cavity 1082 to increase. The second detecting device 1083 can detect the temperature of the motor cavity 1082, and the controller can obtain the heating condition of the motor 102.

The second detecting device 1083 is a temperature sensor.

Alternatively, in the case where the pressure of the air supply line is greater than or equal to the first preset pressure and less than or equal to the second preset pressure, the controller controls the opening degree of the second regulator valve 107 according to the temperature of the motor chamber 1082.

In this embodiment, under the condition that the pressure of the liquid refrigerant in the air supply line 103 is ensured, the first regulating valve 106 may regulate the flow rate of the first air supply line 1031 in a range where the pressure of the air supply line is greater than or equal to a first preset pressure and less than or equal to a second preset pressure. On this premise, the flow rate of the cooling pipeline 104 can be adjusted by adjusting the opening degree of the second adjusting valve 107, and then the flow rate of the liquid refrigerant flowing to the motor 102 is adjusted, so as to increase the cooling effect of the motor 102.

Alternatively, the opening of the second regulator valve 107 is proportional to the temperature of the motor chamber 1082.

In this embodiment, the higher the temperature of the motor cavity 1082 is, the larger the opening degree of the second regulating valve 107 is, the refrigerant flow rate of the cooling pipeline 104 is increased, and the cooling pipeline 104 can release more liquid refrigerants to the motor 102, so as to increase the cooling effect of the motor 102. When the temperature of motor chamber 1082 is lower, the aperture of second governing valve 107 reduces, and the refrigerant flow of cooling line 104 reduces, and then reduces the liquid refrigerant that flows to motor 102 department, and it is too many to place the liquid refrigerant that flows to motor 102 department, and the vaporization is not enough, causes the inside hydrops of compressor 10, and then influences the normal operating of compressor 10.

Optionally, the ratio of the opening degree of the second regulating valve 107 is X, the temperature of the motor cavity 1082 is T, and the relationship is: and X is k T + a, wherein k is greater than 0, and a is greater than or equal to 0. Wherein a may be 0 or more than 0.

Alternatively, the inner wall surface of the housing 108 is provided with a spiral groove forming a spiral cooling flow passage 111 with the outer circumferential surface of the stator 1021 of the motor 102, and an inlet end of the spiral cooling flow passage 111 communicates with an outlet end of the cooling pipe 104, wherein the outlet end of the spiral cooling flow passage 111 and the outlet end of the bearing 101 communicate with the accommodating chamber 1081.

In this embodiment, the spiral cooling channel 111 increases the contact area between the liquid refrigerant and the outer peripheral surface of the stator 1021 of the motor 102, so as to improve the cooling effect of the liquid refrigerant on the motor 102.

Optionally, the casing 108 further defines a gas return line 109, the casing 108 is provided with a gas outlet, an inlet end of the gas return line 109 is communicated with the accommodating cavity 1081, and an outlet end of the gas return line 109 is communicated with the gas outlet, so that the gaseous refrigerant after cooling the motor 102 and the gaseous refrigerant after suspending the bearing 101 are exhausted to the outside of the casing 108 through the gas return line 109 and the gas outlet.

In this embodiment, the gas return line 109 enables the gaseous refrigerant in the accommodating cavity 1081 to flow to the outside of the housing 108, so as to avoid the phenomenon that the gaseous refrigerant is gathered in the accommodating cavity 1081 to increase the pressure in the accommodating cavity 1081, which results in the liquid refrigerant of the cooling line 104 and the gas supply line 103 not flowing smoothly or flowing backwards.

Alternatively, the inlet port 110 is disposed at the bottom of the housing 108 and the outlet port is disposed at the top of the housing 108. So as to discharge the gaseous refrigerant smoothly, and further ensure the pressure in the accommodating cavity 1081 to be stable.

Alternatively, the inlet 110 may be disposed at the top of the housing 108, and the outlet may be disposed at the bottom wall of the housing 108. So that the liquid refrigerant flowing from the liquid inlet 110 can flow under the action of gravity, and the energy consumption for driving the liquid refrigerant to flow is reduced.

The number of the bearings 101 is plural, and the plural bearings 101 include a first bearing 1011 and a second bearing 1012, and the first bearing 1011 and the second bearing 1012 are respectively located at both ends of the rotor 1022 to support the rotor 1022.

Optionally, the number of the air supply lines 103 is also multiple, and the number of the air supply lines 103 is equal to the number of the bearings 101 and corresponds to one to ensure air supply for each bearing 101.

Optionally, the liquid inlet 110 is in communication with both the first gas supply line 1031 and the second gas supply line 1032, wherein the first regulating valve 106 comprises a first sub-regulating valve 1061 and a second sub-regulating valve 1062, the first sub-regulating valve 1061 is disposed in the first gas supply line 1031, and the second sub-regulating valve 1062 is disposed in the second gas supply line 1032.

The number of the throttling devices 105 is the same as that of the air supply pipelines 103, and the throttling devices 105 correspond to one another, and each throttling device 105 comprises a second throttling device 1051 and a third throttling device 1052, wherein the second throttling device 1051 is located in the first air supply pipeline 1031, and the third throttling device 1052 is located in the second air supply pipeline 1032.

Optionally, the controller obtains the distances between the liquid inlet 110 and the first bearing 1011 and the second bearing 1012, and controls the opening degrees of the first sub-regulating valve 1061 and the second sub-regulating valve 1062 according to the distances between the liquid inlet 110 and the first bearing 1011 and the second bearing 1012, so that the refrigerant pressure suspending the first bearing 1011 is the same as the refrigerant pressure suspending the second bearing 1012.

For example, the distance between the liquid inlet 110 and the first bearing 1011 is smaller than the distance between the liquid inlet 110 and the second bearing 1012, and the controller may control the opening degree of the first sub-adjusting valve 1061 to be larger than the opening degree of the second sub-adjusting valve 1062, so that the pressure of the refrigerant flowing into the first bearing 1011 is the same as the pressure of the refrigerant flowing into the second bearing 1012, and thus the two ends of the rotor 1022 are balanced, and the smooth operation of the rotor 1022 is ensured.

Optionally, the compressor 10 further includes a third detection device, the third detection device is located at the bottom of the motor cavity 1082, and the third detection device may detect a content of the liquid refrigerant at the bottom of the motor cavity 1082. The controller is connected with the third detection device, and the controller can control the opening degree of the second regulating valve 107 according to the content of the liquid refrigerant at the bottom of the motor cavity 1082.

In this embodiment, if there is liquid refrigerant in the motor cavity 1082, the normal operation of the motor 102 may be affected, and in order to ensure the normal operation of the compressor 10, the controller may control the opening of the second adjusting valve 107 according to the content of the liquid refrigerant at the bottom of the motor cavity 1082, so as to avoid the liquid refrigerant from being accumulated in the motor cavity 1082.

Specifically, when the content of the liquid refrigerant at the bottom of the motor cavity 1082 is greater than the preset content, the controller controls the second adjusting valve 107 to decrease the opening degree, so as to decrease the refrigerant flow of the cooling pipeline 104, and further avoid the liquid refrigerant from continuing to accumulate in the motor cavity 1082.

The preset content is the content of liquid refrigerant capable of being evaporated automatically at the existing temperature in the motor cavity 1082.

Optionally, when the content of the liquid refrigerant at the bottom of the motor cavity 1082 is less than the preset content, the controller may continuously control the opening of the second adjusting valve 107 according to the temperature of the motor cavity 1082.

Alternatively, the third detection device may be a liquid level sensor, a water sensitive sensor, a water immersion sensor, or the like.

The compressor 10 further includes blades provided to the rotor 1022; when the rotor 1022 rotates, the rotor 1022 can drive the blades to rotate, and the blades further drive the liquid refrigerant in the motor cavity 1082 to flow, so as to cool the motor 102.

In this embodiment, the liquid refrigerant enters the motor cavity 1082 through the liquid inlet 110 and then contacts the blades. When the motor 102 is operated, the rotor 1022 rotates, and the rotor 1022 rotates the blades. After the blades are contacted with the liquid refrigerant, the blades can drive the liquid refrigerant to flow, so that the flowing speed of the liquid refrigerant is accelerated, and further the evaporative cooling of the liquid refrigerant is accelerated. Through the driving of the blades, the temperature of the liquid refrigerant is reduced, the contact area between the liquid refrigerant and the motor 102 is increased, the cooling effect of the liquid refrigerant on the motor 102 is further improved, and the full-working-condition cooling of the compressor 10 is realized.

Optionally, the housing 108 and the motor 102 jointly define a refrigerant channel, an inlet end of the refrigerant channel is communicated with the liquid inlet 110, and when the rotor 1022 drives the blade to rotate, the blade can drive the liquid refrigerant to flow in the refrigerant channel; the refrigerant channels include a first refrigerant channel extending along an axial direction of the rotor 1022 and a second refrigerant channel extending along a radial direction of the rotor 1022.

The rotor 1022 can not only drive the liquid refrigerant to accelerate the flowing speed, but also drive the liquid refrigerant to flow in the refrigerant channel. The first refrigerant flow channel extends in the axial direction of the rotor 1022 and can sufficiently cool the stator 1021, and the second refrigerant flow channel extends in the radial direction of the rotor 1022 and can sufficiently cool the rotor 1022. Through the arrangement of the cooling medium flow channel and the blades, the cooling medium can be in sufficient contact with the rotor 1022 and the stator 1021, so that the cooling effect of the motor 102 is increased.

Optionally, a channel extending along the axial direction of the rotor 1022 is disposed in the stator winding, and the first coolant flow channel includes a channel, so that the stator winding can be cooled when a liquid coolant enters the channel.

By adopting the heat dissipation structure for the compressor of the embodiment, the first refrigerant flow channel comprises a channel penetrating through the stator winding, the blades drive the liquid refrigerant to enter the stator winding through the channel, the liquid refrigerant can be in direct contact with the coil of the stator winding, and the refrigerant can evaporate to take away the heat of the coil through the coil of the stator winding, so that the stator winding is cooled.

Optionally, the first cooling medium flow channel further includes a spiral cooling flow channel 111 to increase a flow area of the cooling medium, so as to increase a contact area between the cooling medium and the stator 1021 and the rotor 1022, and further increase a cooling effect of the cooling medium on the motor 102 in the motor cavity 1082.

Alternatively, as shown in fig. 13, the number of the blades is multiple, the multiple blades include multiple first blades 801, the multiple first blades 801 are sequentially arranged on the outer circumferential surface of the first end of the rotor 1022 at intervals in the circumferential direction of the rotor, the first ends of the first blades are connected with the outer circumferential surface of the first end of the rotor 1022, and the first ends of the first blades are inclined toward a first direction along the direction from the stator winding 1023 to the first end of the rotor, and the first direction is the direction in which the rotor 1022 rotates; when the rotor 1022 rotates, the first blade 801 can drive the liquid refrigerant to flow in the first liquid refrigerant channel, so that the liquid refrigerant passes through the first refrigerant channel from the first end of the rotor and reaches the second end of the rotor.

The first blade 801 is obliquely disposed on the outer peripheral surface of the first end of the rotor, and when the first blade 801 rotates along with the rotor 1022, the first blade 801 can drive the liquid refrigerant to flow along the first refrigerant channel. With the arrangement, the flow speed of the liquid refrigerant can be increased, and the contact area between the liquid refrigerant and the stator 1021 can be increased, so that the cooling effect of the liquid refrigerant on the motor 102 is increased.

Alternatively, the first plurality of blades 801 are sequentially and evenly spaced along the outer circumferential surface of the first end of the rotor.

In this embodiment, the first blades 801 are uniformly disposed, so that the liquid refrigerant in the first refrigerant channel can uniformly flow, and the liquid refrigerant can uniformly dissipate heat of the motor 102.

Alternatively, as shown in fig. 14, the plurality of blades includes a plurality of second blades 802, the plurality of second blades 802 are sequentially disposed at intervals on the outer circumferential surface of the second end of the rotor 1022 in the circumferential direction of the rotor 1022, and the second blades 802 are disposed in parallel with the axis of the rotor 1022; when the rotor 1022 rotates, the second blade 802 can drive the liquid refrigerant to flow in the second refrigerant channel, and the second blade 802 can drive the liquid refrigerant flowing along the axial direction to turn into the second refrigerant channel extending along the radial direction, so as to be discharged out of the compressor 10.

After the first blade 801 drives the liquid refrigerant to flow to the second end of the rotor along the first refrigerant flow channel, the second blade 802 is arranged in parallel with the axis of the rotor 1022, and when the rotor 1022 rotates, the second blade 802 drives the liquid refrigerant to turn to flow from one side of the second end of the rotor to the other side of the second end of the rotor, so that the liquid refrigerant can cool the second end of the rotor, the second seal cavity and the second bearing 1012.

Alternatively, the plurality of second blades 802 are sequentially and uniformly disposed along the outer circumferential surface of the second end of the rotor.

In this embodiment, the second blades 802 are uniformly disposed, so that the liquid refrigerant in the second refrigerant flow channel 804 can uniformly flow, and the liquid refrigerant can uniformly dissipate heat of the motor 102.

Alternatively, as shown in fig. 13, the second blade 802 is arc-shaped, and the opening of the arc is oriented in a first direction, wherein the first direction is the rotation direction of the rotor 1022.

In this embodiment, the second blade 802 is disposed in an arc shape, which increases the contact area between the second blade 802 and the liquid refrigerant, so that when the second blade 802 rotates along with the rotor 1022, more liquid refrigerant can be driven to flow, thereby increasing the flow rate of the liquid refrigerant in the second refrigerant flow channel, and improving the cooling effect of the second refrigerant flow channel on the motor 102.

The embodiment of the present disclosure further provides a liquid supply system of a compressor, where the liquid supply system of the compressor includes the compressor 10 and a main refrigerant loop in any one of the above embodiments, the main refrigerant loop is provided with a liquid taking port, and the liquid taking port is communicated with the liquid inlet 110 through a liquid taking pipeline 30.

The liquid supply system of the compressor according to the embodiment of the present disclosure includes the compressor 10 according to any one of the above embodiments, so that the liquid supply system has all the advantages of the compressor 10 according to any one of the above embodiments, and details are not repeated herein.

Optionally, the liquid-taking port is disposed in the condenser 20, a liquid refrigerant in the condenser 20 can flow into the liquid-taking pipeline 30 through the liquid-taking port and then enter the compressor 10 through the liquid inlet 110, and the liquid refrigerant can be changed into a gaseous refrigerant in the compressor 10 to suspend the bearing 101 and cool the motor 102.

By adopting the liquid supply system of the compressor of the embodiment, the liquid refrigerant is directly taken from the condenser 20 and directly supplied to the interior of the compressor 10, so that the components such as an air supply tank for supplying air outside the compressor 10, a heating device and the like are saved, the energy consumption is saved, and the system is optimized.

Optionally, the liquid refrigerant flowing in through the liquid inlet 110 is a high-pressure liquid refrigerant, and the pressure of the high-pressure liquid refrigerant can satisfy the pressure required by the suspension of the bearing 101, so as to reduce the pressure adjustment of the liquid refrigerant entering the compressor 10.

Optionally, the liquid taking pipeline 30 includes a first liquid taking pipeline 301, the first liquid taking pipeline 301 is communicated between the liquid inlet 110 and the liquid taking port, and the liquid refrigerant in the condenser 20 can autonomously flow into the compressor 10 through the first liquid taking pipeline 301 under the action of a pressure difference between the condenser 20 and the compressor 10.

By adopting the liquid supply system of the compressor of the embodiment, since the condenser 20 is the highest position of the liquid refrigerant pressure in the main refrigerant circuit, the liquid refrigerant is directly taken from the condenser 20 and enters the compressor 10, and when the pressure in the condenser 20 is greater than the pressure in the compressor 10, the liquid refrigerant can automatically flow into the compressor 10 from the first liquid taking pipeline 301 under the action of the pressure difference between the condenser 20 and the compressor 10. By the arrangement, the arrangement of the driving device of the liquid taking pipeline 30 is saved, the system is optimized, and the energy consumption is saved.

Optionally, under the condition that the pressure of the liquid refrigerant in the condenser is greater than the pressure of the liquid inlet 110 of the compressor 10, the liquid refrigerant of the condenser 20 may autonomously flow into the liquid inlet 110 through the liquid taking port and the first liquid taking pipeline 301, and then enter the inside of the compressor 10, without a driving device, which saves energy consumption.

Since the liquid inlet 110 is communicated with the bearing 101, and the pressure at the liquid inlet 110 is greater than or equal to the pressure at the bearing 101, the pressure of the liquid refrigerant in the condenser 20 is also greater than or equal to the pressure of the bearing 101 under the condition that the pressure of the liquid refrigerant in the condenser is greater than the pressure of the liquid inlet 110 of the compressor 10. In this embodiment, when the pressure of the liquid refrigerant in the condenser is greater than the pressure of the liquid inlet 110 of the compressor 10, the liquid refrigerant in the condenser 20 may automatically flow into the liquid inlet 110 through the liquid taking port and the first liquid taking pipeline 301, and then flow to the bearing 101.

Optionally, the liquid taking pipeline 30 further includes a second liquid taking pipeline 302 and a pressurizing device 3022, the second liquid taking pipeline 302 is connected in parallel with the first liquid taking pipeline 301; the pressurizing device 3022 is disposed on the second liquid-fetching pipe 302, and the pressurizing device 3022 can pressurize the liquid refrigerant flowing out from the liquid-fetching port, and drive the pressurized liquid refrigerant to flow into the liquid inlet 110 through the second liquid-fetching pipe 302 and then enter the compressor 10.

With the liquid supply system of the compressor of the embodiment, when the pressure in the condenser 20 is low, such as during the start-up stage of the compressor 10 or when the temperature of the cooling water is low, the pressure in the condenser 20 is low, so that the liquid refrigerant in the condenser 20 cannot directly flow into the compressor 10 or the pressure of the liquid refrigerant in the condenser 20 does not satisfy the pressure required by the bearing 101. The pressurizing device 3022 of the second liquid-extracting pipeline 302 can pressurize the liquid refrigerant flowing out of the condenser 20 and then send the liquid refrigerant into the compressor 10, so as to ensure that the pressure of the liquid refrigerant meets the pressure required by the bearing 101, thereby ensuring the normal operation of the compressor 10.

Alternatively, the pressurizing device 3022 may be a refrigerant pump, a gear pump, or the like, and may pressurize the liquid refrigerant and drive the liquid refrigerant to flow through the first liquid extraction pipe 301.

Optionally, the liquid supply system of the compressor further comprises a first solenoid valve 3011, a second solenoid valve 3021, a fourth detection device, and a controller.

The first solenoid valve 3011 is disposed on the first liquid extraction pipeline 301 and can control on/off of the first liquid extraction pipeline 301. The second electromagnetic valve 3021 is provided in the second liquid extraction pipe 302 and can control the on/off of the second liquid extraction pipe 302. The fourth detection device is arranged on the condenser 20 and used for detecting the pressure of the liquid refrigerant in the condenser; the controller is connected with the first solenoid valve 3011, the second solenoid valve 3021 and the fourth detection device, and the controller can receive the pressure of the condenser 20 and can control the opening and closing of the first solenoid valve 3011 and the second solenoid valve 3021 according to the pressure of the condenser 20 to control the opening and closing of the first liquid taking pipeline 301 and the second liquid taking pipeline 302.

With the liquid supply system of the compressor according to this embodiment, the controller may control the first solenoid valve 3011 and the second solenoid valve 3021 to open and close according to the pressure of the liquid refrigerant in the condenser 20, so as to control the on/off of the first liquid extraction pipeline 301 and the second liquid extraction pipeline 302. When the compressor is used, the opening and closing of the first electromagnetic valve 3011 and the second electromagnetic valve 3021 can be adjusted as required, so that the pressure of the liquid refrigerant entering the compressor 10 meets the requirement, the flexibility of liquid refrigerant supply is increased, and the normal operation of the compressor 10 is fully ensured.

The fourth sensing device is a pressure sensor and is installed inside the condenser 20.

As shown in fig. 9, an embodiment of the present disclosure provides a control method for a liquid supply system of a compressor, including:

s901, the controller acquires the pressure of the liquid refrigerant in the condenser.

S902, the controller controls the opening and closing of the first solenoid valve 3011 and the second solenoid valve 3021 according to the pressure of the liquid refrigerant in the condenser.

In this embodiment, the controller may control the first solenoid valve 3011 and the second solenoid valve 3021 to be opened and closed according to the pressure of the liquid refrigerant in the condenser 20, and further control the first liquid-taking line 301301 and the second liquid-taking line 302302 to be opened and closed. When the compressor is used, the opening and closing of the first electromagnetic valve 3011 and the second electromagnetic valve 3021 can be adjusted as required, so that the pressure of the liquid refrigerant entering the compressor 10 meets the requirement, the flexibility of liquid refrigerant supply is increased, and the normal operation of the compressor 10 is fully ensured.

Optionally, the controller is configured to: when the pressure of the liquid refrigerant in the condenser is greater than or equal to a fifth preset pressure, the first electromagnetic valve 3011 is controlled to be opened and the second electromagnetic valve 3021 is controlled to be closed, so that the first liquid taking pipeline 301 is connected and the second liquid taking pipeline 302 is disconnected; the fifth preset pressure is greater than the pressure of the liquid inlet 110, so that the liquid refrigerant of the condenser 20 can flow into the compressor 10 through the first liquid taking pipeline 301 under the action of the pressure difference between the condenser 20 and the compressor 10.

With the liquid supply system of the compressor of this embodiment, when the pressure of the liquid refrigerant in the condenser is greater than or equal to the fifth preset pressure, the liquid refrigerant in the condenser 20 can automatically flow into the compressor 10 under the pressure difference between the condenser 20 and the compressor 10. The controller controls the first liquid taking pipeline 301 to be communicated with the second liquid taking pipeline 302 and disconnected, the pressurizing device 3022 is not needed to work, and the energy consumption of a liquid supply system of the compressor is saved.

Optionally, when the compressor 10 normally operates, the minimum pressure required by the bearing 101 is a seventh preset pressure, and the fifth preset pressure is greater than the seventh preset pressure, so that the suspension of the bearing 101 can be ensured after the liquid refrigerant enters the compressor 10.

Optionally, in practical applications, pressure of the liquid refrigerant flowing from the liquid taking port to the bearing 101 is lost, and a pressure loss value of the liquid refrigerant flowing from the liquid taking port to the bearing 101 is an eighth preset pressure. The fifth preset pressure is greater than or equal to the sum of the seventh preset pressure and the eighth preset pressure, so that the pressure of the liquid refrigerant flowing into the bearing 101 is prevented from being less than the seventh preset pressure due to the loss of the liquid refrigerant in the liquid taking pipeline 30, and the pressure of the liquid refrigerant flowing into the bearing 101 from the condenser 20 is ensured to be within the pressure range required by the bearing 101.

Therefore, when the pressure of the liquid refrigerant in the condenser is greater than or equal to the fifth preset pressure, the liquid refrigerant in the condenser 20 can automatically flow into the compressor 10 under the action of the pressure difference, and the pressure of the refrigerant entering the bearing 101 can be ensured to be greater than the seventh preset pressure required by the bearing 101.

Alternatively, the pressure device 3022 is connected to a controller, which is capable of controlling the operation of the pressure device 3022 according to the pressure of the condenser 20; when the pressure of the liquid refrigerant in the condenser is lower than the fifth preset pressure, the controller controls the first solenoid valve 3011 to close and the second solenoid valve 3021 to open, so that the first liquid-extracting pipeline 301 is disconnected and the second liquid-extracting pipeline 302 is connected, and controls the pressurizing device 3022 to operate to pressurize the liquid refrigerant in the second liquid-extracting pipeline 302.

With the liquid supply system of the compressor according to this embodiment, when the pressure of the liquid refrigerant in the condenser is smaller than the pressure of the liquid intake port or the pressure of the liquid refrigerant in the condenser 20 flowing into the bearing 101 through the first liquid intake pipeline 301 is smaller than the seventh preset pressure, the controller controls the second liquid intake pipeline 302 to be conducted and controls the pressurizing device 3022 to operate. With the arrangement, on one hand, the liquid refrigerant of the condenser 20 can be ensured to flow into the compressor 10; on the other hand, the pressure of the liquid refrigerant flowing into the bearing 101 is prevented from being lower than the seventh preset pressure due to the loss of the liquid refrigerant in the liquid taking pipeline 30, so as to ensure that the pressure of the liquid refrigerant flowing into the bearing 101 from the condenser 20 is within the pressure range required by the bearing 101.

As shown in fig. 10, another control method for a liquid supply system of a compressor is provided in an embodiment of the present disclosure, including:

s1001, the controller obtains the pressure of the liquid refrigerant in the condenser.

S1002, judging whether the pressure of the liquid refrigerant in the condenser is larger than or equal to a fifth preset pressure by the controller;

and S1003, under the condition that the pressure of the liquid refrigerant in the condenser is greater than or equal to a fifth preset pressure, the controller controls the first electromagnetic valve 3011 to be opened and the second electromagnetic valve 3021 to be closed.

S1004, when the pressure of the liquid refrigerant in the condenser is lower than the fifth preset pressure, the controller controls the first solenoid valve 3011 to close and the second solenoid valve 3021 to open, and controls the operation of the pressurizing device 3022.

By adopting the control method for the liquid supply system of the compressor of the embodiment, the liquid refrigerant of the condenser 20 can be ensured to flow into the compressor 10; and the pressure of the liquid refrigerant flowing into the bearing 101 is less than the third preset pressure due to the loss of the liquid refrigerant in the liquid taking pipeline 30, so as to ensure that the pressure of the liquid refrigerant flowing into the bearing 101 from the condenser 20 is within the pressure range required by the bearing 101.

Optionally, the liquid supply system of the compressor further comprises a pressure regulating valve 304, a fifth detection device 306 and a controller.

The pressure regulating valve 304 is arranged on the liquid taking pipeline 30 and is used for regulating the pressure of the liquid refrigerant in the liquid taking pipeline 30; the fifth detection device 306 is arranged along the flowing direction of the liquid refrigerant in the liquid taking pipeline 30, the pressure regulating valve 304 and the fifth detection device 306 are sequentially arranged on the liquid taking pipeline 30, and the fifth detection device 306 is used for detecting the pressure of the liquid taking pipeline behind the pressure regulating valve; and the controller is connected with the fifth detection device 306 and the pressure regulating valve 304, and can receive the pressure of the liquid taking pipeline 30 behind the pressure regulating valve 304 and control the pressure regulating valve 304 to work according to the pressure of the liquid taking pipeline behind the pressure regulating valve.

With the liquid supply system of the compressor of this embodiment, the pressure regulating valve 304 may regulate the liquid refrigerant in the liquid taking pipe 30 again, so as to prevent the pressure of the liquid refrigerant entering the compressor 10 from being too high to damage the bearing 101 and/or the motor 102.

The fifth sensing device 306 is a pressure sensor.

As shown in fig. 11, another control method for a liquid supply system of a compressor is provided in an embodiment of the present disclosure, including:

s1101, the controller obtains the pressure of the liquid taking pipeline behind the pressure regulating valve.

And S1102, the controller regulates the pressure regulating valve 304 to work according to the pressure of the liquid taking pipeline behind the pressure regulating valve.

The pressure regulating valve 304 can regulate the liquid refrigerant in the liquid taking pipe 30 again to avoid the pressure of the liquid refrigerant entering the compressor 10 from being too high to damage the bearing 101 and/or the motor 102.

Optionally, in a case that the pressure of the liquid taking pipeline 30 after the pressure regulating valve 304 is greater than the sixth preset pressure, the controller controls the pressure regulating valve 304 to operate to reduce the pressure of the liquid taking pipeline 30 after the pressure regulating valve 304; wherein the sixth preset pressure is greater than the fifth preset pressure.

With the liquid supply system of the compressor of this embodiment, when the pressure of the liquid-taking pipe 30 behind the pressure regulating valve 304 is greater than the sixth preset pressure, the pressure of the liquid-state refrigerant in the liquid-taking pipe 30 is too high, which may easily damage the bearing 101 and/or the motor 102, and the controller controls the pressure regulating valve 304 to operate, so as to reduce the pressure of the liquid-state refrigerant in the liquid-taking pipe 30, and further make the pressure of the liquid-state refrigerant entering the compressor 10 within a required range.

As shown in fig. 12, another control method for a liquid supply system of a compressor according to an embodiment of the present disclosure includes:

s1201, the controller obtains the pressure of the liquid taking pipeline behind the pressure regulating valve.

S1202, under the condition that the pressure of the liquid taking pipeline behind the pressure regulating valve is larger than a sixth preset pressure, the controller controls the pressure regulating valve 304 to work so as to reduce the pressure of the liquid taking pipeline behind the pressure regulating valve; wherein the sixth preset pressure is greater than the fifth preset pressure.

When the pressure of the liquid-taking pipeline 30 behind the pressure regulating valve 304 is higher than the sixth preset pressure, the pressure of the liquid refrigerant in the liquid-taking pipeline 30 is too high, which may damage the bearing 101 and/or the motor 102, and the controller controls the pressure regulating valve 304 to operate, so as to reduce the pressure of the liquid-taking pipeline 30, and further, the pressure of the liquid refrigerant entering the compressor 10 is within a required range.

When the compressor 10 is normally operated, the maximum pressure required by the bearing 101 is the tenth preset pressure.

Alternatively, in the case that there is a pressure loss when the liquid refrigerant flows from the pressure regulating valve 304 to the bearing 101, the pressure loss when the liquid refrigerant flows from the pressure regulating valve 304 to the bearing 101 is a ninth preset pressure, and the sixth preset pressure is smaller than the sum of the tenth preset pressure and the ninth preset pressure, so as to ensure that the pressure of the liquid refrigerant flowing into the bearing 101 is within the pressure range required by the bearing 101.

Alternatively, when there is no pressure loss or the pressure loss is almost not considered when the liquid refrigerant flows from the pressure regulating valve 304 to the bearing 101, the sixth preset pressure may be smaller than the tenth preset pressure, so as to sufficiently ensure that the pressure of the liquid refrigerant flowing into the bearing 101 does not exceed the tenth preset pressure.

Optionally, the liquid supply system of the compressor further includes a filter 303 and a check valve 305, the filter 303 is disposed on the liquid taking pipe 30, and the check valve 305 is disposed on the liquid taking pipe 30; the filter 303, the pressure regulating valve 304, and the check valve 305 are provided in this order along the flow direction of the liquid refrigerant in the liquid-taking line 30.

By adopting the liquid supply system of the compressor of the embodiment, the filter 303 can filter impurities in the liquid refrigerant, and prevent the impurities from entering the compressor 10 and damaging the compressor 10. The check valve 305 prevents the liquid refrigerant from flowing backward, thereby ensuring unidirectional flow of the liquid refrigerant in the liquid extraction pipe 30. Along the flowing direction of the liquid refrigerant in the liquid taking pipeline 30, the filter 303, the pressure regulating valve 304 and the check valve 305 are sequentially arranged, the filter 303 can protect the pressure regulating valve 304, and the check valve 305 is close to the compressor 10, so that the liquid refrigerant can be effectively prevented from flowing back to protect the pressure regulating valve 304 and other devices.

Alternatively, a fifth sensing device 306 may be provided on the check valve 305 to sense the pressure in the fluid line 30 after the pressure regulating valve 304. In this embodiment, the installation of the fifth detecting device 306 is facilitated, and the accuracy of the pressure detection of the liquid taking pipeline 30 by the fifth detecting device 306 is increased.

The filter 303 may be a dry filter.

Optionally, the condenser 20 includes a sac 201, and the liquid taking port is provided in the sac 201.

In this embodiment, the condenser 20 is the highest point of the liquid refrigerant in the main refrigerant circuit, and the liquid bag 201 is the highest point of the liquid refrigerant in the condenser 20, so the liquid bag 201 is the highest point of the liquid refrigerant in the main refrigerant circuit. The liquid refrigerant is taken from the liquid bag 201, so that the pressure of the liquid refrigerant can be ensured to the greatest extent, on one hand, the flow of the liquid refrigerant in the first liquid taking pipeline 301 is ensured, on the other hand, the energy consumption of the pressurizing device 3022 is saved, and the energy consumption of a liquid supply system of the whole compressor is further reduced.

When the main refrigerant loop normally operates, the pressure of the liquid refrigerant at the liquid bag 201 is high, so that the conduction times of the second liquid taking pipeline 302 are greatly reduced, the opening times and time of the pressurizing device 3022 are also reduced, and the pipeline design is greatly optimized.

Alternatively, a liquid extraction port may be provided in the evaporator 40, and liquid is extracted from the evaporator 40 through the liquid extraction line 30 and flows into the liquid inlet 110. Since the evaporator 40 has a low pressure of the liquid refrigerant, the liquid-taking pipe 30 is provided with a pressurizing member to pressurize the liquid refrigerant in the liquid-taking pipe 30 and then flow into the compressor 10.

Optionally, the liquid supply system of the compressor further includes an exhaust pipe 701, and the exhaust pipe 701 is communicated between an exhaust port of the compressor 10 and the evaporator 40 to exhaust the working gaseous refrigerant in the compressor 10, so as to form a pressure difference, thereby ensuring that the liquid refrigerant can smoothly enter the compressor 10.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A compressor, comprising:

the cooling device comprises a shell (108) which defines a containing cavity (1081), a cooling pipeline (104) and an air supply pipeline (103) which are arranged in parallel, wherein the shell (108) is provided with a liquid inlet (110);

the motor (102) is positioned in the accommodating cavity (1081) and communicated with the liquid inlet (110) through the cooling pipeline (104), and liquid refrigerant enters the cooling pipeline (104) through the liquid inlet (110) to cool the motor (102);

the bearing (101) is positioned in the accommodating cavity (1081) and communicated with the liquid inlet (110) through the air supply pipeline (103), and liquid refrigerant enters the air supply pipeline (103) through the liquid inlet (110) and changes from liquid state to gas state in the air supply pipeline (103) so as to suspend the bearing (101).

2. The compressor of claim 1, further comprising:

and the throttling device (105) is arranged on the air supply pipeline (103) and is used for changing the liquid refrigerant of the air supply pipeline (103) into the gas refrigerant.

3. The compressor of claim 1,

the number of the liquid inlets (110) is one or more, when the number of the liquid inlets (110) is one, the cooling pipeline (104) and the air supply pipeline (103) are both communicated with the liquid inlets (110), so that after liquid refrigerants flow into the liquid inlets (110), a part of the liquid refrigerants flow into the cooling pipeline (104), and the other part of the liquid refrigerants flow into the air supply pipeline (103).

4. The compressor of claim 3, further comprising:

the pressure adjusting device is arranged on the air supply pipeline (103) and used for adjusting the pressure of the air supply pipeline (103).

5. The compressor of claim 4, wherein the pressure regulating device comprises:

the first regulating valve (106) is arranged on the gas supply pipeline (103), and the first regulating valve (106) can regulate the flow of liquid refrigerant of the gas supply pipeline (103) so as to regulate the pressure of the gas supply pipeline (103);

the compressor (10) further comprises:

the second regulating valve (107) is arranged on the cooling pipeline (104) and is used for regulating the flow of the liquid refrigerant of the cooling pipeline (104);

the first detection device is arranged on the air supply pipeline (103) and used for detecting the pressure of the air supply pipeline;

and the controller is connected with the first regulating valve (106), the second regulating valve (107) and the first detection device, and can receive the pressure of the air supply pipeline and regulate the opening degree of the first regulating valve (106) and the opening degree of the second regulating valve (107) according to the pressure of the air supply pipeline.

6. The compressor of claim 5,

the controller is configured to:

in the case that the pressure of the gas supply line is less than a first preset pressure, the controller controls the second regulating valve (107) to decrease the opening degree, and controls the first regulating valve (106) to increase the opening degree to increase the pressure of the gas supply line;

the controller controls the second regulating valve (107) to increase the opening degree and controls the first regulating valve (106) to decrease the opening degree to reduce the pressure of the gas supply pipeline under the condition that the pressure of the gas supply pipeline is greater than a second preset pressure;

the controller controls the first regulating valve (106) to maintain the opening degree to maintain the pressure of the gas supply line when the pressure of the gas supply line is greater than or equal to the first preset pressure and less than or equal to the second preset pressure;

wherein the first preset pressure is less than the second preset pressure.

7. The compressor of claim 6, wherein the housing cavity (1081) includes a motor cavity (1082), the motor (102) being located within the motor cavity (1082), the compressor further comprising:

the second detection device (1083) is arranged in the motor cavity (1082) and used for detecting the temperature of the motor cavity (1082);

the controller is connected with the second detection device (1083), and the controller can receive the temperature of the motor cavity (1082);

the controller is configured to:

and under the condition that the pressure of the air supply pipeline (103) is greater than or equal to the first preset pressure and less than or equal to the second preset pressure, the controller controls the opening degree of the second regulating valve (107) according to the temperature of the motor cavity (1082).

8. The compressor of claim 7,

the controller is configured to:

the opening degree of the second regulating valve (107) is in proportion to the temperature of the motor cavity (1082).

9. The compressor of any one of claims 1 to 8,

a spiral groove is formed in the inner wall surface of the shell (108), a spiral cooling flow channel (111) is formed by the spiral groove and the outer peripheral surface of a stator (1021) of the motor (102), the inlet end of the spiral cooling flow channel (111) is communicated with the outlet end of the cooling pipeline (104), and the outlet end of the spiral cooling flow channel (111) and the outlet end of the bearing (101) are communicated with the accommodating cavity (1081);

the shell (108) further defines a gas return pipeline (109), the shell (108) is provided with a gas exhaust port, the inlet end of the gas return pipeline (109) is communicated with the accommodating cavity (1081), and the outlet end of the gas return pipeline (109) is communicated with the gas exhaust port, so that gaseous refrigerant after the motor (102) is cooled and gaseous refrigerant after the bearing (101) is suspended are exhausted to the outside of the shell (108) through the gas return pipeline (109) and the gas exhaust port.

10. A liquid supply system for a compressor, comprising:

a compressor according to any one of claims 1 to 9;

and the main refrigerant loop is provided with a liquid taking port, and the liquid taking port is communicated with the liquid inlet (110) through a liquid taking pipeline (30).