WO2023087786A1

WO2023087786A1 - Heat dissipation structure for compressor and compressor

Info

Publication number: WO2023087786A1
Application number: PCT/CN2022/109937
Authority: WO
Inventors: 杨明威; 张捷; 陈远; 顾超
Original assignee: 青岛海尔空调电子有限公司; 青岛海尔空调器有限总公司; 海尔智家股份有限公司
Priority date: 2021-11-22
Filing date: 2022-08-03
Publication date: 2023-05-25
Also published as: CN114251251B; CN114251251A

Abstract

The present application relates to the technical field of refrigeration devices, and discloses a heat dissipation structure for a compressor, comprising: a housing that defines a motor cavity having a liquid inlet through which a liquid-state refrigerant can enter the motor cavity; a motor that is located in the motor cavity, the motor comprising a rotor, and the rotor being rotatably located in the motor cavity; and blades that are provided on the rotor. When the rotor rotates, the rotor can drive the blades to rotate, and the blades then drive the liquid-state refrigerant in the motor cavity to flow, so as to cool the motor. The cooling effect of the refrigerant on the motor is increased, and all condition cooling of the compressor is implemented. The present application also discloses a compressor.

Description

Heat dissipation structure for compressor and compressor

This application is based on a Chinese patent application with application number 202111386887.9 and a filing date of November 22, 2021, and claims the priority of this Chinese patent application. The entire content of this Chinese patent application is hereby incorporated by reference into this application.

technical field

The present application relates to the technical field of refrigeration equipment, for example, to a heat dissipation structure for a compressor and the compressor.

Background technique

Currently, in high-speed compressors, the motor generates a large amount of heat during operation of the compressor. In the related art, liquid refrigerant can be provided inside the compressor to cool the motor.

In the prior art, a motor refrigerant cooling structure is disclosed, including a machine base, a stator core and a rotor core, the stator core is assembled inside the machine base through interference fit, the rotor core is arranged inside the stator core, and the machine base is provided with a refrigerant The inlet and the refrigerant flow channel connected to the refrigerant inlet are used for the flow of the refrigerant to cool the outer surface of the stator core. The first side of the stator core is provided with a first cavity for receiving the refrigerant flowing out from the outlet of the refrigerant flow channel. An air gap is formed between the stator core and the rotor core for the refrigerant in the first cavity to flow in to cool the inner surface of the stator core and the outer surface of the rotor core.

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

After the refrigerant enters the refrigerant flow channel, the temperature of the refrigerant in the refrigerant flow channel cannot be adjusted. If the temperature of the refrigerant entering the unit is high, the cooling effect of the refrigerant on the motor will be poor, and the compressor cannot be cooled under full working conditions.

Contents of the invention

In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is presented below. The summary is not intended to be an extensive overview nor to identify key/important elements or to delineate the scope of these embodiments, but rather serves as a prelude to the detailed description that follows.

Embodiments of the present disclosure provide a heat dissipation structure for a compressor and the compressor, so as to reduce the temperature of the refrigerant entering the interior of the compressor, thereby improving the cooling effect of the refrigerant on the motor, and realizing cooling of the compressor under all working conditions.

An embodiment of the present disclosure provides a heat dissipation structure for a compressor. The heat dissipation structure for a compressor includes: a casing defining a motor chamber with a liquid inlet, through which liquid refrigerant can enter the The motor cavity; the motor is located in the motor cavity, the motor includes a rotor, and the rotor is rotatably located in the motor cavity; the blade is arranged on the rotor; wherein, when the rotor rotates, the The rotor can drive the blades to rotate, and the blades further drive the flow of liquid refrigerant in the cavity of the motor to cool the motor.

An embodiment of the present disclosure further provides a compressor, including the heat dissipation structure for a compressor as described in any one of the above embodiments.

The heat dissipation structure for the compressor and the compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

The blades can move with the rotation of the rotor, and after the liquid refrigerant comes into contact with the blades, the blades can drive the refrigerant to flow. The flow velocity of the liquid refrigerant is increased, the evaporative cooling of the refrigerant is accelerated, and the temperature of the liquid refrigerant is reduced. At the same time, the blades drive the flow of the refrigerant, which also increases the contact area between the refrigerant and the motor, increasing the cooling effect of the motor. The heat dissipation structure for the compressor of this embodiment increases the cooling effect of the refrigerant on the motor, and realizes the cooling of the compressor under all working conditions.

The foregoing general description and the following description are exemplary and explanatory only and are not intended to limit the application.

Description of drawings

One or more embodiments are exemplified by the corresponding drawings, and these exemplifications and drawings do not constitute a limitation to the embodiments, and elements with the same reference numerals in the drawings are shown as similar elements, The drawings are not limited to scale and in which:

Fig. 1 is a schematic structural diagram of a compressor liquid supply system provided by an embodiment of the present disclosure;

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

Fig. 3 is a schematic cross-sectional structural diagram of a compressor provided by an embodiment of the present disclosure;

Fig. 4 is a schematic cross-sectional structural diagram of another compressor provided by an embodiment of the present disclosure;

Fig. 5 is a schematic diagram of a cooperation structure between a first blade and a rotor provided by an embodiment of the present disclosure;

Fig. 6 is a schematic diagram of a cooperation structure between a second blade and a rotor provided by an embodiment of the present disclosure.

Reference signs:

10. Compressor; 101. Bearing; 1011. First bearing; 1012. Second bearing; 102. Motor; 1021. Stator; 1022. Rotor; 1023. Stator winding; 103. Air supply pipeline; 1031. First air supply pipe 1032, the second air supply pipeline; 104, the cooling pipeline (the first cooling pipeline); 105, the throttling device (the first throttling device); 1051, the second throttling device; 10511, the first subsection Flow device; 10512, second sub-throttle device; 108, shell; 1082, motor cavity; 109, exhaust port; 110, liquid inlet; 111, spiral cooling channel; 20, condenser; 201, liquid bag ; 30, the liquid intake pipeline; 301, the first liquid intake pipeline; 3011, the first solenoid valve; 302, the second liquid intake pipeline; 3021, the second solenoid valve; 3022, the pressurizing device; 303, the filter ; 304, pressure regulating valve; 305, check valve; 40, evaporator; 50, third throttling device; 60, refrigerant pipeline; 701, exhaust pipeline; 80, blade; 801, first blade; 802 , the second blade; 803, the first refrigerant flow channel; 804, the second refrigerant flow channel.

Detailed ways

In order to understand the characteristics and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below in conjunction with the accompanying drawings. The attached drawings are only for reference and description, and are not intended to limit the embodiments of the present disclosure. In the following technical description, 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 simplified in order to simplify the drawings.

The terms "first", "second" and the like in the description and claims of the embodiments of the present disclosure and the above drawings are used to distinguish similar objects, and are not necessarily used to describe a specific sequence or sequence. It should be understood that the data so used may be interchanged under appropriate circumstances so as to facilitate the embodiments of the disclosed embodiments described herein. Furthermore, the terms "comprising" and "having", as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the orientations or positional relationships indicated by the terms "upper", "lower", "inner", "middle", "outer", "front", "rear" etc. are based on the orientations or positional relationships shown in the drawings. Positional relationship. These terms are mainly used to better describe the embodiments of the present disclosure and their implementations, and are not used to limit that the indicated devices, elements or components must have a specific orientation, or be constructed and operated in a specific orientation. Moreover, some of the above terms may be used to indicate other meanings besides orientation or positional relationship, for example, the term "upper" may also be used to indicate a certain attachment relationship or connection relationship in some cases. Those skilled in the art can understand the specific meanings of these terms in the embodiments of the present disclosure according to specific situations.

In addition, the terms "setting", "connecting" and "fixing" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediary, or two devices, components or Internal connectivity between components. Those skilled in the art can understand the specific meanings of the above terms in the embodiments of the present disclosure according to specific situations.

Unless stated otherwise, the term "plurality" means two or more.

The term "and/or" is an associative relationship describing objects, indicating that there can be three relationships. For example, A and/or B means: A or B, or, A and B, these three relationships.

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

As shown in FIG. 3 and FIG. 4 , an embodiment of the present disclosure provides a compressor 10. The compressor 10 includes a casing 108 and a motor 102. The motor 102 is located in a motor cavity 1082. The motor 102 includes a stator 1021 and a rotor 1022. The stator 1021 is set There is a mounting seat on which the rotor 1022 is rotatably mounted. The main function of the stator 1021 is to generate a rotating magnetic field, and the main function of the rotor 1022 is to be cut by the magnetic force lines in the rotating magnetic field to generate (output) current. The stator 1021 includes a stator core, a stator winding 1023 and a frame, and the stator winding 1023 is embedded in the stator core.

The stator winding 1023 refers to the winding installed on the stator 1021, that is, the copper wire wound on the stator core. The stator winding 1023 is a general term for a phase or the entire electromagnetic circuit formed by a plurality of coils or coil groups.

The compressor 10 further includes a bearing 101 for supporting the rotation of the rotor 1022 , wherein the rotor 1022 protrudes out of the housing 108 through the housing 108 , and the bearing 101 is supported between the rotor 1022 and the housing 108 . The bearing 101, the housing 108, the rotor 1022 and the stator 1021 together form a sealed cavity.

Wherein, the bearing 101 comprises a first bearing 1011 and a second bearing 1012, the first bearing 1011 is supported between the first end of the rotor and the housing 108, the first bearing 1011, the first end of the rotor, the housing 108 and the stator 1021 jointly form a first sealed cavity. The second bearing 1012 is supported between the second end of the rotor and the housing 108 , and the second bearing 1012 , the second end of the rotor, the housing 108 and the stator 1021 together form a second sealed cavity.

As shown in FIG. 3 to FIG. 6 , an embodiment of the present disclosure provides a heat dissipation structure for a compressor. The heat dissipation structure for a compressor includes a housing 108 , a motor 102 and a blade 80 . The housing 108 defines a liquid inlet The motor cavity 1082 of the port 110, the liquid refrigerant can enter the motor cavity 1082 through the liquid inlet 110; the motor 102 is located in the motor cavity 1082, the motor 102 includes a rotor 1022, and the rotor 1022 is rotatably located in the motor cavity 1082; the blade 80 is arranged in the rotor 1022; Wherein, when the rotor 1022 rotates, the rotor 1022 can drive the blades 80 to rotate, and the blades 80 further drive the liquid refrigerant in the motor chamber 1082 to cool the motor 102 .

With the heat dissipation structure for the compressor of this embodiment, the liquid refrigerant enters the motor cavity 1082 through the liquid inlet 110 and contacts the blade 80 . When the motor 102 is working, the rotor 1022 rotates, and the rotor 1022 drives the blade 80 to rotate. After the blade 80 contacts with the liquid refrigerant, it will drive the liquid refrigerant to flow, speed up the flow speed of the liquid refrigerant, and then accelerate the evaporative cooling of the liquid refrigerant. Driven by the blades 80 , not only the temperature of the liquid refrigerant is reduced, but also the contact area between the liquid refrigerant and the motor 102 is increased, thereby improving the cooling effect of the liquid refrigerant on the motor 102 and realizing cooling of the compressor 10 under all working conditions.

Optionally, the casing 108 and the motor 102 jointly define a refrigerant channel, the inlet end of the refrigerant channel communicates with the liquid inlet 110, and when the rotor 1022 drives the blade 80 to rotate, the blade 80 can drive the liquid refrigerant to flow in the refrigerant channel Wherein, the refrigerant channel includes a first refrigerant channel 803 extending axially along the rotor 1022 and a second refrigerant channel 804 extending radially along the rotor 1022 .

Arrows in FIGS. 3 and 4 indicate the flow direction of the refrigerant.

With the heat dissipation structure for the compressor of this embodiment, the rotor 1022 can not only drive the liquid refrigerant to speed up the flow speed, but also drive the liquid refrigerant to flow in the refrigerant channel. The first refrigerant channel 803 extends along the axial direction of the rotor 1022 to sufficiently cool the stator 1021 , and the second refrigerant channel 804 extends along the radial direction of the rotor 1022 to sufficiently cool the rotor 1022 . Through the arrangement of the refrigerant channel and the vane 80, the refrigerant can fully contact the rotor 1022 and the stator 1021, so as to increase the cooling effect of the motor 102.

Optionally, a channel extending axially along the rotor 1022 is provided in the stator winding 1023 , the first refrigerant flow channel 803 includes a channel, and the stator winding 1023 can be cooled when the liquid refrigerant enters the channel.

With the heat dissipation structure for the compressor of this embodiment, the first refrigerant channel 803 includes a channel passing through the stator winding 1023, and the blade 80 drives the liquid refrigerant through the channel to enter the stator winding 1023, and can directly contact the coil of the stator winding 1023 The refrigerant passing through the coil of the stator winding 1023 can evaporate and take away the heat of the coil, thereby cooling the stator winding 1023 .

Optionally, a second passage is defined between the inner surface of the stator 1021 and the outer surface of the rotor 1022 , and the second passage extends along the axial direction of the rotor 1022 , wherein the first refrigerant flow passage 803 further includes the second passage.

In this embodiment, the vane 80 can not only drive the liquid refrigerant to flow in the stator winding 1023 through the channel to cool the coil, but also drive the liquid refrigerant to flow in the second channel to cool the inner surface of the stator 1021 and the outer surface of the rotor 1022 . Such setting increases the circulation area of the refrigerant, further increases the contact area between the refrigerant and the stator 1021 and the rotor 1022 , and further increases the cooling effect of the refrigerant on the motor 102 in the motor cavity 1082 .

Optionally, as shown in FIG. 5 , there are multiple blades 80 , the multiple blades 80 include multiple first blades 801 , and the multiple first blades 801 are sequentially arranged at intervals along the circumference of the rotor 1022 on the first blade of the rotor. The outer peripheral surface of the end, the first end of the first blade is connected to the outer peripheral surface of the first end of the rotor 1022, along the direction from the stator winding 1023 to the first end of the rotor, the first end of the first blade is inclined towards the first direction , the first direction is the direction in which the rotor 1022 rotates; wherein, 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 from the first end of the rotor The runner 803 then reaches the second end of the rotor.

With the heat dissipation structure for the compressor of this embodiment, the first blade 801 is obliquely arranged on the outer peripheral surface of the first end of the rotor, and when the first blade 801 rotates with the rotor 1022, it can drive the liquid refrigerant along the first refrigerant flow path 803 flow. Such arrangement can not only increase the flow velocity of the liquid refrigerant, but also increase the contact area between the liquid refrigerant and the stator 1021 , so as to increase the cooling effect of the liquid refrigerant on the motor 102 .

Optionally, a plurality of first blades 801 are sequentially and evenly spaced along the outer peripheral surface of the first end of the rotor.

In this embodiment, a plurality of first vanes 801 are evenly arranged, so that the liquid refrigerant in the first refrigerant channel 803 can flow evenly, so that the liquid refrigerant can evenly dissipate heat to the motor 102 .

Optionally, as shown in FIG. 6, the plurality of blades 80 includes a plurality of second blades 802, and the plurality of second blades 802 are sequentially arranged at intervals on the outer peripheral surface of the second end of the rotor along the circumferential direction of the rotor 1022, and the second blades 802 is set parallel to the axis of the rotor 1022; wherein, when the rotor 1022 rotates, the second vane 802 can drive the liquid refrigerant to flow in the second refrigerant channel 804, and the second vane 802 can drive the liquid refrigerant flowing in the axial direction to turn into the The radially extending second refrigerant channel 804 is used to discharge the compressor 10 .

With the heat dissipation structure for the compressor of this embodiment, the first blade 801 drives the liquid refrigerant to flow along the first refrigerant channel 803 to the second end of the rotor, the second blade 802 is arranged parallel to the axis of the rotor 1022, and the rotor 1022 When rotating, the second vane 802 drives the liquid refrigerant to turn 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 flow to the second end of the rotor, the second sealed cavity and the second bearing 1012 Allow to cool.

Optionally, a plurality of second vanes 802 are evenly arranged in sequence along the outer peripheral surface of the second end of the rotor.

In this embodiment, a plurality of second blades 802 are evenly arranged, so that the liquid refrigerant in the second refrigerant channel 804 can flow evenly, so that the liquid refrigerant can evenly dissipate heat to the motor 102 .

Optionally, as shown in FIG. 6 , the second blade 802 is arc-shaped, and the arc-shaped opening faces a first direction, wherein the first direction is the rotation direction of the rotor 1022 .

In this embodiment, the second vane 802 is arranged in an arc shape, which increases the contact area between the second vane 802 and the liquid refrigerant, so that when the second vane 802 rotates with the rotor 1022, it can drive more liquid refrigerant to flow. The flow rate of the liquid refrigerant in the second refrigerant flow channel 804 is increased to improve the cooling effect of the second refrigerant flow channel 804 on the motor 102 .

Optionally, as shown in Figures 3 and 4, the casing 108 is also provided with an exhaust port 109, and the exhaust port 109 is arranged at the bottom of the casing 108; wherein, the liquid inlet 110 is arranged at the top of the casing 108 , so that the liquid refrigerant can enter the motor chamber 1082 under the action of gravity, and can move along the radial direction of the rotor 1022 .

In this embodiment, the liquid inlet 110 is located at the top of the housing 108 , and the exhaust port 109 is located at the bottom of the housing 108 . After the liquid refrigerant enters the motor chamber 1082 through the top of the housing 108 , a part of the liquid refrigerant continues to move to the bottom of the housing 108 under the action of gravity. The part of the liquid refrigerant moves along the radial direction of the rotor 1022 from one side of the first end of the rotor to the other side of the first end of the rotor to cool the first end of the rotor, the first bearing 1011 and the first sealed cavity. cool down. The other part of the liquid refrigerant is driven by the first blade 801 from the first end of the rotor through the first refrigerant channel 803 and reaches the second end of the rotor, and then under the action of the second blade 802 and gravity, the liquid refrigerant flows from the rotor One side of the second end of the rotor moves to the other side of the second end of the rotor to cool the second end of the rotor, the second bearing 1012 and the second sealed cavity. The cooling structure for the compressor of this embodiment can completely cool the motor 102 , improve the cooling effect, and realize the cooling of the compressor 10 under all working conditions.

Optionally, the heat dissipation structure for the compressor further includes a shaft sleeve, on which a plurality of blades 80 are arranged at intervals along the axial direction of the shaft sleeve, and the shaft sleeve can be sleeved on the outer peripheral surface of the rotor 1022 .

The shaft sleeve includes a first shaft sleeve and a second shaft sleeve. A plurality of first blades 801 are arranged on the first shaft sleeve, and the plurality of first blades 801 are sequentially arranged at intervals along the circumferential direction of the first shaft sleeve. The plurality of second blades 802 is disposed on the second sleeve, and a plurality of second vanes 802 are sequentially arranged at intervals along the circumferential direction of the second sleeve.

Optionally, the blade 80 is detachably connected to the rotor 1022 .

In this embodiment, the blade 80 is detachably connected to the rotor 1022 , which facilitates maintenance and replacement of the blade 80 . Moreover, when the motor 102 is turned on, the temperature of the motor 102 is relatively low, and when cooling is not required, the blades 80 may not be connected to the rotor 1022 , so as to save the energy consumption of the rotor 1022 rotating.

Optionally, the rotor 1022 is electromagnetically connected to the blade 80 .

In this embodiment, the rotor 1022 and the blade 80 can be controlled to be powered on and off according to the requirement, and then the rotor 1022 and the blade 80 can be controlled to be adsorbed or separated.

Optionally, the sleeve is detachably connected to the rotor 1022 .

For example, the shaft sleeve and the rotor 1022 are electromagnetically connected, wherein the rotor 1022 is provided with a mounting hole, the shaft sleeve is provided with a connecting pin, and the connecting pin and the shaft sleeve are connected by a spring, so that the connecting pin can perform telescopic movement relative to the shaft sleeve . Wherein, the connecting pin is adapted to the mounting hole, and when the connecting pin is located in the mounting hole, the sleeve is connected to the rotor 1022 so that the blade 80 is mounted on the rotor 1022 .

Wherein, when the connecting pin is located inside the mounting hole, the spring is in an initial state, and when the connecting pin is located outside the mounting hole, the spring is in a deformed state. The shaft sleeve includes an electromagnetic device. When the electromagnetic device is energized, the electromagnetic device generates a magnetic force, and the electromagnetic device attracts the connecting pin to move toward the shaft sleeve, so that the connecting pin is separated from the mounting hole. At this time, the sleeve is separated from the rotor 1022 , and the blade 80 is also separated from the rotor 1022 . When the electromagnetic device is powered off, there is no magnetic force between the bushing and the connecting pin, and the connecting pin can enter the installation hole under the action of the spring, thereby realizing the connection between the bushing and the rotor 1022, and the blade 80 is also connected to the rotor 1022. connect.

Optionally, the blade 80 and the rotor 1022 may also be fixedly connected.

In this embodiment, the blade 80 is fixedly connected to the rotor 1022 , which increases the stability of the blade 80 when the rotor 1022 rotates, and prevents the blade 80 from falling off and affecting the normal operation of the compressor 10 .

Optionally, the casing 108 defines a cooling pipeline 104 (hereinafter collectively referred to as the first cooling pipeline 104 for ease of distinction), and the first cooling pipeline 104 communicates with the liquid inlet 110 and the motor cavity 1082; The heat dissipation structure also includes a throttling device 105 (hereinafter collectively referred to as the first throttling device 105 for the sake of distinction), the first throttling device 105 is arranged on the first cooling pipeline 104, and is used to change the liquid refrigerant into a gas-liquid mixed state refrigerant, so that the gas-liquid mixed state refrigerant enters the motor chamber 1082.

In this embodiment, the first throttling device 105 turns the liquid refrigerant into a mist-like gas-liquid mixed refrigerant and then sprays it into the motor chamber 1082 to increase the contact area between the refrigerant and the blade 80 and facilitate the driving effect of the blade 80 on the refrigerant .

Optionally, the first throttling device 105 may be a capillary device, a micro orifice, and the like.

Optionally, the cooling structure for the compressor further includes a second regulating valve, and the second regulating valve is arranged in the first cooling pipeline 104 for adjusting the flow rate of the liquid refrigerant in the first cooling pipeline 104 .

Optionally, along the flow direction of the liquid refrigerant in the first cooling pipeline 104, the second regulating valve and the first throttling device 105 are arranged in sequence.

Optionally, as shown in Fig. 3 and Fig. 4, an embodiment of the present disclosure further provides a compressor 10, including a heat dissipation structure for a compressor according to any one of the above embodiments.

The compressor 10 provided in the embodiments of the present disclosure includes all the beneficial effects of the heat dissipation structure for compressors in any of the above embodiments because it includes the heat dissipation structure for compressors in any of the above embodiments, I won't repeat them here.

In FIG. 3 and FIG. 4 , the arrows with thick solid lines indicate the flow direction of the liquid refrigerant in the air supply pipeline 103 and the cooling pipeline 104, and the arrows with thin solid lines indicate the flow direction of the refrigerant in the first refrigerant flow channel 803 and the second refrigerant flow channel 804. Flow direction.

Optionally, the compressor 10 includes, but is not limited to, an air suspension compressor, a magnetic suspension compressor, a centrifugal compressor, a gas-liquid hybrid bearing compressor, a shaft-lifting compressor with a gas refrigerant or a liquid refrigerant, and the like. The compressor shown in Figure 3 is suitable for compressors that do not require air supply, such as magnetic levitation compressors and centrifugal compressors. The compressor shown in Figure 4 is suitable for air suspension compressors, gas-liquid hybrid bearing compressors, gas refrigerant or liquid refrigerant shaft-lifting compressors that require gas supply, and the like. It can be understood that the compressor shown in Figure 3 is also applicable to air suspension compressors, gas-liquid hybrid bearing compressors, gas refrigerant or liquid refrigerant shaft-lifting compressors that require air supply, and the like.

Optionally, the casing 108 also defines an air supply pipeline 103 , the air supply pipeline 103 communicates with the liquid inlet 110 and the bearing 101 , and the liquid refrigerant changes into a gas refrigerant in the air supply pipeline 103 to support the bearing 101 .

The gaseous refrigerant in the gas supply pipeline 103 can be directly obtained from the outside through the gas supply pipeline 103, without relying only on the gaseous refrigerant generated after the motor 102 is cooled by the liquid refrigerant in the first cooling pipeline 104, thereby ensuring the gas entering the bearing 101, To ensure the stability of the air supply to the bearing 101.

Optionally, the number of liquid inlets 110 can be multiple, and the plurality of liquid inlets 110 include a first liquid inlet and a second liquid inlet, the first liquid inlet 110 is in communication with the gas supply pipeline 103, and the second The liquid inlet 110 communicates with the first cooling pipeline 104 .

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

Optionally, when the number of the liquid inlet 110 is one, the first cooling pipeline 104 and the air supply pipeline 103 are both connected to the liquid inlet 110, wherein, after the liquid refrigerant flows into the liquid inlet 110, a part of the liquid refrigerant enters The first cooling pipeline 104 is used to cool the motor 102 , and another part of the liquid refrigerant enters the air supply pipeline 103 , and changes from liquid to gas in the air supply pipeline 103 to suspend the bearing 101 .

With the compressor 10 of this embodiment, after the liquid refrigerant passes through the liquid inlet 110 , part of the liquid refrigerant enters the first cooling pipeline 104 to cool the motor 102 to ensure the normal operation of the motor 102 of the compressor 10 . Another part of the liquid refrigerant enters the air supply pipeline 103 and changes from liquid to gas in the air supply pipeline 103 to suspend the bearing 101 . In the compressor 10 of the embodiment of the present disclosure, one liquid inlet 110 can be used to feed the suspension bearing 101 and the cooling compressor 10 at the same time, which facilitates the connection of the external liquid extraction pipeline 30 and facilitates the installation of the compressor 10 .

Optionally, as shown in FIG. 4 , the compressor 10 further includes a second throttling device 1051 , and the second throttling device 1051 is disposed on the gas supply pipeline 103 for changing the liquid refrigerant in the gas supply pipeline 103 into a gas refrigerant.

In the embodiment of the present disclosure, the liquid refrigerant in the air supply pipeline 103 is throttled by the second throttling device 1051 and becomes a gaseous refrigerant, and the gaseous refrigerant is supplied to the bearing 101 to suspend the bearing 101 . The second throttling device 1051 is provided in the air supply pipeline 103 , which can save the heating device, etc., and reduce the energy consumption of the compressor 10 .

Optionally, the second throttling device 1051 includes a micro orifice, a capillary throttling device, and the like.

The principle of throttling by the throttling device is: the liquid refrigerant will form a local contraction at the throttling device, so that the flow rate of the liquid refrigerant increases and the static pressure decreases, so a static pressure difference is generated before and after the throttling device. Furthermore, the pressure of the liquid refrigerant is reduced gradually to become a gas refrigerant, and the gas refrigerant can suspend the bearing 101 .

In practical applications, since the compressor 10 is working, the bearing 101 will also generate heat, and the liquid refrigerant in the air supply pipeline 103 can also flow directly to the bearing 101, and the liquid refrigerant can exchange heat with the bearing 101. After the heat exchange, the liquid refrigerant into a gaseous refrigerant. Such arrangement can not only supply air to the bearing 101 , but also cool the bearing 101 to ensure the normal operation of the bearing 101 and further ensure the reliable movement of the compressor 10 .

In some cases, the liquid refrigerant will become a gas-liquid mixed mist refrigerant after passing through the second throttling device 1051 , and the mist refrigerant can not only support the suspension bearing 101 , but also cool the bearing 101 .

Optionally, the compressor 10 further includes a communication pipeline, which connects the first 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 first cooling pipeline 104 cools down the motor 102 and absorbs the heat of the motor 102 , it is vaporized into a gaseous refrigerant, and the pressure in the first cooling pipeline 104 increases. The gaseous refrigerant enters the air supply pipeline 103 through the communication pipeline. On the one hand, the pressure in the first cooling pipeline 104 can be reduced, so that the liquid refrigerant can circulate normally. On the other hand, the gas supply pipeline 103 is replenished with gaseous refrigerant through the communication pipeline, the air pressure in the gas supply pipeline 103 is increased, the bearing 101 is suspended, and the compressor 10 works normally.

By adopting this optional embodiment, the refrigerant can be used more rationally, the utilization rate of the gaseous refrigerant can be improved, the energy consumption of the compressor 10 can be reduced, and the use cost can be reduced.

Optionally, the compressor 10 further includes an injection device, which is arranged on the gas supply pipeline 103, and the communication pipeline communicates with the gas supply pipeline 103 through the injection device.

The communication pipeline communicates with the gas supply pipeline 103 through the injection device. In the injection device, the gaseous refrigerant provided by the communication pipeline ejects the liquid refrigerant in the gas supply pipeline 103, so that the liquid refrigerant in the gas supply pipeline 103 becomes 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 and the compressor 10 operates normally.

Optionally, along the flow direction of the refrigerant in the air supply pipeline 103 , the injection device and the second throttling device 1051 are arranged in sequence.

Optionally, the compressor 10 further includes a pressure regulating device, which is provided in the gas supply pipeline 103 and used to adjust the pressure of the gas supply pipeline.

In the embodiment of the present disclosure, the pressure regulating device can adjust the pressure of the liquid refrigerant in the air supply pipeline 103 to ensure that the pressure of the liquid refrigerant flowing to the second throttling device 1051 meets the demand, so that the pressure of the liquid refrigerant passing through the second throttling The pressure of the refrigerant throttled by the device 1051 meets the suspension pressure of the bearing 101 .

Optionally, the pressure regulating device includes a first regulating valve, the first regulating valve is arranged in the gas supply pipeline 103, and the first regulating valve can adjust the flow rate of the liquid refrigerant in the gas supply pipeline 103 to adjust the pressure of the gas supply pipeline.

In this embodiment, the gas supply pipeline 103 is defined by the casing 108 of the compressor 10, so the pipeline area of the gas supply pipeline 103 is fixed, and the first regulating valve can adjust the flow rate of the liquid refrigerant in the gas supply pipeline 103, wherein, As the flow rate of the liquid refrigerant increases, the flow rate also increases, and the pressure of the liquid refrigerant also increases. Similarly, when the flow rate of the liquid refrigerant decreases, the flow rate also decreases, and the pressure of the liquid refrigerant also decreases.

The compressor 10 also includes a second regulating valve, a first detection device and a controller; the second regulating valve is arranged on the first cooling pipeline 104, and is used to adjust the flow rate of the liquid refrigerant in the first cooling pipeline 104; the first detection device is provided in the gas supply pipeline 103 to detect the pressure of the gas supply pipeline.

Optionally, when the number of the liquid inlet 110 is one, the controller is connected to the first regulating valve, the first regulating valve and the first detection device, and the controller can receive the pressure of the gas supply pipeline, and according to The pressure of the air supply line regulates the opening degrees of the first regulating valve and the opening degrees of the second regulating valve.

In this embodiment, when the amount of liquid refrigerant flowing in through the liquid inlet 110 remains unchanged, the pressures of the gas supply pipeline 103 and the first cooling pipeline 104 are adjusted through the first regulating valve and the second regulating valve, thereby enabling The pressure of the refrigerant flowing to the bearing 101 is adjusted to 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.

Optionally, when the pressure of the gas supply pipeline is lower than the first preset pressure, the controller controls the opening of the second regulating valve to decrease, and controls the first regulating valve to increase the opening to increase the pressure of the gas supply pipeline.

In this embodiment, when the air supply pipeline 103 is less than the first preset pressure, the pressure of the liquid refrigerant in the air supply pipeline 103 is relatively small, which will cause the pressure of the refrigerant flowing to the bearing 101 to be too small to suspend the bearing 101, so The opening of the second regulating valve is controlled to decrease to reduce the refrigerant flow rate of the first cooling pipeline 104 . At the same time, the opening of the first regulating valve is controlled to increase the flow rate of the air supply pipeline 103 to increase the pressure of the refrigerant in the air supply pipeline 103 to ensure that the pressure of the refrigerant flowing to the bearing 101 can suspend the bearing 101 .

Optionally, when the pressure of the gas supply pipeline is greater than the second preset pressure, the controller controls the opening of the second regulating valve to increase, and controls the first regulating valve to decrease the opening to reduce the pressure of the gas supply pipeline.

In this embodiment, when the pressure of the air supply pipeline 103 is greater than the second preset pressure, the pressure of the liquid refrigerant in the air supply pipeline 103 is relatively high, which will cause the pressure of the refrigerant flowing to the bearing 101 to be relatively high, causing damage to the bearing 101. Therefore, the opening degree of the second regulating valve is controlled to increase to increase the refrigerant flow rate of the first cooling pipeline 104 . At the same time, the opening of the first regulating valve is controlled to reduce the flow rate of the air supply pipeline 103, so as to reduce the pressure of the refrigerant in the air supply pipeline 103, so as to ensure that the pressure of the refrigerant flowing to the bearing 101 can not only suspend the bearing 101, but also The bearing 101 will be damaged.

Optionally, the first regulating valve is a solenoid valve or a pressure regulating valve 304 and the like, and the second regulating valve is a solenoid valve or a flow regulating valve and the like.

Optionally, when the pressure of the gas supply pipeline 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 of the first regulating valve to maintain the pressure of the gas supply pipeline; wherein , the first preset pressure is less than the second preset pressure.

In this embodiment, when the pressure of the gas supply pipeline 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 gas supply pipeline 103 after flowing to the bearing 101 is higher than that of the bearing 101 Within the required pressure range, not only the bearing 101 can be suspended, but also the bearing 101 will not be damaged. The controller controls the opening of the pressure regulating valve 304 to maintain the pressure of the refrigerant in the air supply pipeline 103 .

Optionally, the first preset pressure may be the minimum critical value of the pressure required by the bearing 101 , and the second preset pressure may be the maximum critical value of the pressure required by the bearing 101 . The minimum limit value of the pressure required by the bearing 101 is the third preset pressure, and the maximum limit value of the pressure required by the bearing 101 is the fourth preset pressure. Wherein, the third preset pressure is lower than the first preset pressure, and the fourth preset pressure is higher than the second preset pressure.

In this embodiment, considering that it takes time for the liquid refrigerant in the gas supply pipeline 103 to flow to the bearing 101 after the pressure is adjusted, especially during the start-up phase of the compressor 10, there is no gaseous refrigerant at the bearing 101. In order to avoid insufficient pressure of the gaseous refrigerant at the bearing 101, The third preset pressure is lower than the first preset pressure, so as to ensure that the bearing 101 will not be damaged when the adjusted liquid refrigerant flows to the bearing 101 . Similarly, in order to prevent the pressure of the gaseous refrigerant at the bearing 101 from being too high, when the pressure of the gas supply pipeline reaches the second preset pressure, the controller timely reduces the pressure of the liquid refrigerant in the gas supply pipeline 103 to prevent the bearing 101 from being under the required pressure. The maximum limit value to cause damage to the bearing 101.

Optionally, the compressor 10 also includes a second detection device, the second detection device is arranged in the motor cavity 1082, and is used to detect the temperature of the motor cavity 1082; the controller is connected with the second detection device, and the controller can receive the motor cavity 1082 temperature.

In this embodiment, 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. During the rotation of the rotor 1022, both the stator 1021 and the rotor 1022 will generate heat, which will cause the motor cavity 1082 temperature rise. By detecting the temperature of the motor chamber 1082 through the second detecting device, the controller can obtain the heating condition of the motor 102 .

The second detection device is a temperature sensor.

Optionally, when the pressure of the air supply pipeline 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 according to the temperature in the motor cavity 1082 .

In this embodiment, under the condition that the pressure of the liquid refrigerant in the gas supply pipeline 103 is guaranteed, the first regulating valve can operate in the range where the pressure of the gas supply pipeline is greater than or equal to the first preset pressure and less than or equal to the second preset pressure. Internally adjust the flow rate of the first air supply pipeline 1031. Under this premise, the flow rate of the first cooling pipeline 104 can be adjusted by adjusting the opening of the second regulating valve, and then the flow rate of the liquid refrigerant flowing to the motor 102 can be adjusted to increase the cooling effect of the motor 102 .

Optionally, the opening degree of the second regulating valve is directly proportional to the temperature of the motor cavity 1082 .

In this embodiment, the higher the temperature of the motor cavity, the larger the opening of the second regulating valve, the greater the refrigerant flow rate of the first cooling pipeline 104, and the first cooling pipeline 104 can release more liquid refrigerant to the motor 102 , to increase the cooling effect of the motor 102. When the temperature of the motor cavity is low, the opening degree of the second regulating valve is reduced, and the refrigerant flow rate of the first cooling pipeline 104 is reduced, thereby reducing the liquid refrigerant flowing to the motor 102 and preventing the liquid refrigerant flowing to the motor 102 If it is too much, the vaporization will not be sufficient, resulting in liquid accumulation inside the compressor 10, thereby affecting the normal operation of the compressor 10.

Optionally, the opening degree of the second regulating valve is X, the temperature of the motor cavity 1082 is T, and the relationship between X and T is: X=k*T+a, where k>0, a≥0. a can be greater than 0 or equal to 0.

Optionally, the casing 108 also defines a second cooling pipeline, and the second cooling pipeline communicates with the liquid inlet 110. Optionally, the inner wall of the casing 108 is provided with a spiral groove, and the spiral groove is connected to the motor 102. The outer peripheral surface of the stator 1021 forms a spiral cooling channel 111 , the inlet end of the spiral cooling channel 111 communicates with the liquid outlet of the second cooling pipeline, and the outlet end of the spiral cooling channel 111 communicates with the motor cavity 1082 .

In this embodiment, the second cooling pipeline is used to cool the outer surface of the stator 1021, and 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, thereby improving the liquid refrigerant to the motor 102. For the cooling effect, the liquid refrigerant flows into the motor cavity 1082 after being cooled by the spiral cooling channel 111 , and then is discharged from the motor cavity 1082 through the exhaust port 109 .

Optionally, the housing 108 also defines a third cooling pipeline 104, the outlet end of the third cooling pipeline 104 communicates with the inlet end of the first cooling pipeline 104 and the inlet end of the second cooling pipeline, and the second The inlet end of the third cooling pipeline 104 communicates with the liquid inlet 110 . It can be understood that: the liquid refrigerant first enters the third cooling pipeline 104 through the liquid inlet 110, and then splits at the outlet end of the third cooling pipeline 104, part of it flows into the first cooling pipeline 104, and the other part flows into the second cooling pipeline road.

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 can detect the 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 according to the content of the liquid refrigerant at the bottom of the motor cavity 1082 .

In this embodiment, if there is liquid refrigerant accumulated in the motor chamber 1082, it will affect the normal operation of the motor 102. In order to ensure the normal operation of the compressor 10, the controller can control the second regulating valve according to the content of the liquid refrigerant at the bottom of the motor chamber 1082. The opening degree is to avoid accumulation of liquid refrigerant in the motor cavity 1082 .

Specifically, when the liquid refrigerant content at the bottom of the motor chamber 1082 is greater than the preset content, the controller controls the second regulating valve to reduce the opening to reduce the refrigerant flow rate of the first cooling pipeline 104, thereby preventing the liquid refrigerant from continuing to flow in the motor chamber 1082. memory volume.

Wherein, the preset content is the content of the liquid refrigerant that can evaporate by itself at the existing temperature in the motor chamber 1082 .

Optionally, when the liquid refrigerant content at the bottom of the motor chamber 1082 is less than the preset content, the controller may continue to control the opening of the second regulating valve according to the temperature of the motor chamber 1082 .

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

There are multiple bearings 101 , the multiple 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 two ends of the rotor 1022 to support the rotor 1022 .

Optionally, the number of air supply pipelines 103 is also multiple, and the number of air supply pipelines 103 is equal to and corresponds to the number of bearings 101 , so as to ensure the air supply of each bearing 101 .

Optionally, the liquid inlet 110 communicates with both the first gas supply pipeline 1031 and the second gas supply pipeline 1032, wherein the first regulating valve includes a first sub-regulating valve and a second sub-regulating valve, and the first sub-regulating valve It is installed in the first air supply pipeline 1031 , and the second sub-regulator valve is installed in the second air supply pipeline 1032 .

The number of the second throttling device 1051 is the same as the number of the gas supply pipeline 103 and corresponds one by one. The throttling device 105 includes a first sub-throttling device 10511 and a second sub-throttling device 10512. The first sub-throttling device 10511 is located at In the first gas supply pipeline 1031 , the second sub-throttling device 10512 is located in the second gas supply pipeline 1032 .

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

As shown in Figures 1 and 2, an embodiment of the present disclosure also provides a liquid supply system for a compressor. The liquid supply system for a compressor includes the compressor 10 and the main refrigerant circuit of any one of the above embodiments, and the main refrigerant circuit A liquid intake port is provided, and the liquid intake port communicates with the liquid inlet port 110 through the liquid intake pipeline 30 .

The liquid supply system of the compressor in the embodiments of the present disclosure includes the compressor 10 in any one of the above-mentioned embodiments, so it has all the beneficial effects of the compressor 10 in any one of the above-mentioned embodiments, and will not be repeated here.

The arrows in Fig. 1 and Fig. 2 indicate the flow direction of the refrigerant in the liquid supply system of the compressor.

An embodiment of the present disclosure provides a liquid supply system for a compressor. The liquid supply system for a compressor includes a main refrigerant circuit, and the main refrigerant circuit includes a compressor 10 , a condenser 20 , and a third throttling device connected through a refrigerant pipeline 60 50 and evaporator 40. 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 60 , and the compressor 10 compresses the low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant, and then passes the second refrigerant pipeline 60 to compress the high-temperature and high-pressure gaseous refrigerant. The gaseous refrigerant is delivered to the condenser 20. The high-temperature and high-pressure gaseous refrigerant becomes a liquid refrigerant at normal temperature and high pressure after the condenser 20 dissipates heat.

The normal temperature and high pressure liquid refrigerant returns to the evaporator 40 after passing through the third refrigerant pipeline and the third throttling device 50 . Wherein, the room-temperature and high-pressure liquid refrigerant reaches the evaporator 40 from the third throttling device 50 and the space suddenly increases, the pressure decreases, and the liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant. The low-temperature and low-pressure liquid refrigerant will be vaporized in the evaporator 40 to become a low-temperature and low-pressure gaseous refrigerant. After that, the evaporator 40 transmits the low-temperature and low-pressure gaseous refrigerant to the compressor 10 again through the first refrigerant pipeline to complete the refrigeration cycle.

Optionally, the liquid supply system of the compressor also includes an exhaust pipeline 701, which communicates with the exhaust port 109 and the evaporator 40, so as to cool the gaseous refrigerant inside the compressor 10 and/or supply the gas The gaseous refrigerant is delivered to the inside of the evaporator 40 .

Optionally, the liquid intake port is arranged in the condenser 20, and the liquid refrigerant in the condenser 20 can flow into the liquid intake pipeline 30 through the liquid intake port, and then enter the interior of the compressor 10 through the liquid intake port 110, and the liquid refrigerant in the compressor 10 The interior can be turned into a gaseous refrigerant to suspend the bearing 101 and cool the motor 102 .

Adopting the liquid supply system of the compressor of this embodiment, the liquid refrigerant is directly taken from the condenser 20 and directly supplied to the interior of the compressor 10, which saves components such as an air supply tank and a heating device for supplying air outside the compressor 10, and saves energy. Consumption, optimize the system.

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 meet the pressure required for the bearing 101 to suspend, so as to reduce the pressure adjustment of the liquid refrigerant entering the compressor 10 .

Optionally, the condenser 20 includes a liquid bag 201 , and the liquid intake port is arranged on the liquid bag 201 .

In this embodiment, the condenser 20 is the point with the highest pressure of the liquid refrigerant in the main refrigerant circuit, and the liquid bag 201 is the point with the highest pressure of the liquid refrigerant in the condenser 20, so the liquid bag 201 is the point with the highest pressure in the main refrigerant circuit. Taking the liquid refrigerant from the liquid bag 201 can ensure the pressure of the liquid refrigerant to the greatest extent. On the one hand, it ensures the flow of the liquid refrigerant in the first liquid extraction pipeline 301. On the other hand, it saves the energy consumption of the pressurizing device 3022, thereby reducing The energy consumption of the liquid supply system of the entire compressor.

Since the pressure of the liquid refrigerant at the liquid bladder 201 is relatively high when the main refrigerant circuit is in normal operation, the number of conductions of the second liquid extraction pipeline 302 is greatly reduced, and the number and time of opening the pressurizing device 3022 are greatly reduced. Optimized the Flo design.

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

With the liquid supply system of the compressor of this 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. When the pressure in the condenser 20 is greater than the compression When the internal pressure of the compressor 10 is low, the liquid refrigerant can flow into the compressor 10 autonomously from the first liquid extraction pipeline 301 under the action of the pressure difference between the condenser 20 and the compressor 10 . Such setting saves the setting of the driving device of the liquid-taking pipeline 30, optimizes the system, and saves energy consumption.

Optionally, when the pressure of the liquid refrigerant in the condenser 20 is greater than the pressure of the liquid inlet 110 of the compressor 10, the liquid refrigerant in the condenser 20 can flow into the inlet by itself through the liquid inlet and the first liquid inlet pipeline 301. The liquid port 110 further enters the interior of the compressor 10 without a driving device, which saves energy consumption.

Since the liquid inlet 110 communicates with the bearing 101, the pressure at the liquid inlet 110 is greater than or equal to the pressure at the bearing 101, so the pressure of the liquid refrigerant in the condenser 20 is greater than the pressure at the liquid inlet 110 of the compressor 10. In some cases, the pressure of the liquid refrigerant in the condenser 20 is also greater than or equal to the pressure of the bearing 101 . In this embodiment, when the pressure of the liquid refrigerant in the condenser 20 is greater than the pressure of the liquid inlet 110 of the compressor 10, the liquid refrigerant in the condenser 20 can be autonomously It flows into the liquid inlet 110 and then flows to the bearing 101.

Optionally, the liquid extraction pipeline 30 also includes a second liquid extraction pipeline 302 and a pressurizing device 3022, the second liquid extraction pipeline 302 is arranged in parallel with the first liquid extraction pipeline 301; the pressurizing device 3022 is arranged on the second The liquid intake line 302 and the pressurizing device 3022 can pressurize the liquid refrigerant flowing out through the liquid intake port, and drive the pressurized liquid refrigerant to flow into the liquid inlet 110 through the second liquid intake line 302 and then enter the compressor 10 internal.

Using the liquid supply system of the compressor of this embodiment, when the pressure in the condenser 20 is low, such as when the compressor 10 is started up or the temperature of the cooling water is low, the pressure in the condenser 20 is low, causing the condenser 20 to The liquid refrigerant in the condenser cannot directly flow into the compressor 10 or the pressure of the liquid refrigerant in the condenser 20 does not meet the pressure required by the bearing 101 . The pressurizing device 3022 of the second liquid extraction pipeline 302 can pressurize the liquid refrigerant flowing out of the condenser 20 and then send it into the compressor 10 to ensure that the pressure of the liquid refrigerant meets the pressure required by the bearing 101, thereby ensuring that the compressor 10 for normal operation.

Optionally, the pressurizing device 3022 may be a refrigerant pump, a gear pump, etc., capable of pressurizing the liquid refrigerant and driving the liquid refrigerant to flow in the first liquid extraction pipeline 301 .

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

Optionally, when the pressure of the liquid refrigerant in the condenser 20 is greater than or equal to the fifth preset pressure, the first solenoid valve 3011 is controlled to open and the second solenoid valve 3021 is closed, so that the first liquid-taking pipeline 301 leads to and the second liquid extraction pipeline 302 is disconnected; wherein, the fifth preset pressure is greater than the pressure of the liquid inlet 110, so that the liquid refrigerant in the condenser 20 can be under the pressure difference between the condenser 20 and the compressor 10 , flows into the compressor 10 through the first liquid extraction pipeline 301 .

Using the liquid supply system of the compressor in this embodiment, when the pressure of the liquid refrigerant in the condenser 20 is greater than or equal to the fifth preset pressure, the liquid refrigerant in the condenser 20 can be under the action of the pressure difference between the condenser 20 and the compressor 10 It flows into the inside of the compressor 10 autonomously. The controller controls the first liquid extraction pipeline 301 to be connected to the second liquid extraction pipeline 302 to disconnect, so that the pressurizing device 3022 does not need to work, which saves the energy consumption of the liquid supply system of the compressor.

Optionally, the liquid supply system of the compressor further includes a filter 303, a pressure regulating valve 304 and a check valve 305, and the filter 303, the pressure regulating valve 304 and the check valve 305 are all arranged in the liquid extraction pipeline 30; wherein, Along the flow direction of the liquid refrigerant in the liquid extraction pipeline 30 , a filter 303 , a pressure regulating valve 304 and a check valve 305 are arranged in sequence.

With the liquid supply system of the compressor in this embodiment, the filter 303 can filter impurities in the liquid refrigerant to prevent impurities from entering the compressor 10 and damaging the compressor 10 . The check valve 305 can prevent the liquid refrigerant from flowing back and ensure the one-way flow of the liquid refrigerant in the liquid extraction pipeline 30 . Along the flow direction of the liquid refrigerant in the liquid extraction pipeline 30, a filter 303, a pressure regulating valve 304 and a check valve 305 are arranged in sequence. The filter 303 can protect the pressure regulating valve 304, and the proximity of the check valve 305 to the compressor 10 can effectively avoid The liquid refrigerant returns to protect devices such as the pressure regulating valve 304 .

Optionally, as shown in FIG. 1, the liquid refrigerant can enter the interior of the compressor 10 and then split to flow to the gas supply pipeline 103 and the first cooling pipeline 104, or as shown in FIG. 2, the liquid refrigerant can then enter the compressor 10 front split flow, a part flows into the air supply pipeline 103, and the other part flows into the first cooling pipeline 104.

The above description and drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may incorporate structural and other changes. The examples merely represent possible variations. Individual components and functions are optional unless explicitly required, and the order of operations may vary. Portions and features of some embodiments may be included in or substituted for those of other embodiments. 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

A heat dissipation structure for a compressor, characterized in that it comprises:

The housing (108) defines a motor chamber (1082) having a liquid inlet (110), and liquid refrigerant can enter the motor chamber (1082) through the liquid inlet (110);

a motor (102), located in the motor chamber (1082), the motor (102) including a rotor (1022), the rotor (1022) rotatably located in the motor chamber (1082);

blades (80), arranged on the rotor (1022);

Wherein, when the rotor (1022) rotates, the rotor (1022) can drive the blades (80) to rotate, and the blades (80) further drive the liquid refrigerant in the motor cavity (1082) to flow to cool The motor (102).
The heat dissipation structure for a compressor according to claim 1, characterized in that,

The casing (108) and the motor (102) jointly define a refrigerant flow path, the inlet end of the refrigerant flow path communicates with the liquid inlet (110), and the rotor (1022) drives the When the blade (80) rotates, the blade (80) can drive the liquid refrigerant to flow in the refrigerant channel;

Wherein, the refrigerant flow channel includes a first refrigerant flow channel (803) extending axially along the rotor (1022) and a second refrigerant flow channel (804) extending radially along the rotor (1022).
The heat dissipation structure for a compressor according to claim 2, characterized in that,

The motor (102) also includes a stator winding (1023), the stator winding (1023) is provided with a channel extending axially along the rotor (1022), and the first refrigerant channel (803) includes the channel, and the liquid refrigerant can cool the stator winding (1023) when entering the channel.
The heat dissipation structure for a compressor according to claim 3, characterized in that,

The number of the blades (80) is multiple, and the multiple blades (80) include:

A plurality of first blades (801), the plurality of first blades (801) are sequentially arranged at intervals along the circumferential direction of the rotor (1022) on the outer peripheral surface of the first end of the rotor, the first blades The first end is connected to the outer peripheral surface of the first end of the rotor (1022), along the direction from the stator winding (1023) to the first end of the rotor, the first end of the first blade faces the first The direction is inclined, and the first direction is the direction in which the rotor (1022) rotates;

Wherein, when the rotor (1022) rotates, the first blade (801) can drive the liquid refrigerant to flow in the first refrigerant channel (803), so that the liquid refrigerant passes through the first end of the rotor. After passing through the first refrigerant channel (803), it reaches the second end of the rotor.
The heat dissipation structure for a compressor according to claim 2, characterized in that,

The number of the blades (80) is multiple, and the multiple blades (80) include:

A plurality of second blades (802), the plurality of second blades (802) are sequentially arranged at intervals along the circumferential direction of the rotor (1022) on the outer peripheral surface of the second end of the rotor, and the second blades ( 802) arranged parallel to the axis of the rotor (1022);

Wherein, when the rotor (1022) rotates, the second vane (802) can drive the liquid refrigerant flowing in the axial direction to turn into the second refrigerant channel (804) extending in the radial direction to discharge The compressor (10).
The heat dissipation structure for a compressor according to claim 5, characterized in that,

The second blade (802) is arc-shaped, and the arc-shaped opening faces a first direction, wherein the first direction is the rotation direction of the rotor (1022).
The heat dissipation structure for a compressor according to claim 1, characterized in that,

The housing (108) is also provided with an exhaust port (109), and the exhaust port (109) is located at the bottom of the housing (108);

Wherein, the liquid inlet (110) is arranged on the top of the housing (108), so that liquid refrigerant can enter the motor cavity (1082) under the action of gravity.
The heat dissipation structure for a compressor according to claim 1, characterized in that,

The blade (80) is detachably connected to the rotor (1022); or,

The blades (80) are fixedly connected to the rotor (1022).
The heat dissipation structure for a compressor according to any one of claims 1 to 8, characterized in that,

The casing (108) defines a cooling pipeline (104), and the cooling pipeline (104) communicates with the liquid inlet (110) and the motor chamber (1082);

The heat dissipation structure for the compressor also includes:

The throttling device (105) is arranged in the cooling pipeline (104), and is used to change the liquid refrigerant into a gas-liquid mixed state refrigerant, so that the gas-liquid mixed state refrigerant enters the motor cavity (1082).
A compressor, characterized by comprising the heat dissipation structure for a compressor according to any one of claims 1 to 9.