CN217274535U - Refrigerant compression device, air conditioner outdoor unit and air conditioner - Google Patents

Abstract

The utility model relates to a refrigerant compression device, an air conditioner outdoor unit and an air conditioner, belonging to the technical field of air conditioners, and aims at solving the technical problem that the existing refrigerant compression device is not easy to return oil. The refrigerant compression device includes a compressor and an oil separator. The air outlet of the compressor is connected to the inlet of the oil separator through a first pipeline. The oil separator has a first oil outlet, and the first oil outlet is connected to the compressor through a second pipeline. The suction pipe is connected, and the second pipe is provided with an active control valve. When the refrigerant compression device, the outdoor unit of the air conditioner and the air conditioner of the present invention cannot automatically return the oil by utilizing the fluctuation of the exhaust pressure of the compressor to spontaneously return the oil separated in the oil separator to the compressor, the oil return cannot be performed automatically. The active control valve is opened, so that the separated oil of the oil separator flows from the second pipeline to the suction pipe of the compressor.

Description

Refrigerant Compressor, Air Conditioner Outdoor Unit and Air Conditioner

technical field

The utility model relates to the technical field of air conditioners, in particular to a refrigerant compression device, an air conditioner outdoor unit and an air conditioner.

Background technique

In order to prevent the liquid in the refrigerant from flowing out when the outdoor unit is exhausted, an oil separator is installed in the exhaust pipe of the air conditioner, and the oil separated by the oil separator (hereinafter referred to as the separated oil) is returned to the compressor. However, when the compressor installed in the air conditioner is a high-pressure compressor with the compressor body pressure equal to the discharge pressure, the pressure inside the oil separator will be lower than the compressor body pressure due to pressure loss in the discharge pipe. Therefore, if only the oil return pipe is connected between the oil separator and the compressor body, the separated oil cannot be returned to the compressor.

In order to solve the above problems, the following solutions are adopted in the background art:

(1) As shown in FIG. 1, in the background art 1, the oil separator and the suction pipe 80 of the compressor 10 are connected through the oil return pipe provided with the capillary 99. For example, for a 10hp air conditioner, an inner diameter of 1.0mm can be used, Capillary tube 99 with a length of 700mm. With the above structure, the separated liquid refrigerant can flow from the oil separator 20 to the suction pipe 80 of the compressor 10 with a lower pressure, and then return to the compressor 10 . However, when the above method is used, the gaseous part of the exhaust refrigerant also flows to the intake pipe 80 through the return pipe. As a result, the flow of refrigerant to the indoor unit is reduced, resulting in poor cooling or heating capacity. At the same time, when the high-temperature exhaust refrigerant is mixed into the intake refrigerant, the intake air temperature rises, thereby causing the exhaust temperature to rise, and ultimately, the reliability of the compressor 10 is lowered.

(2) As shown in FIG. 2 , in Background Art 2, the oil separator 20 and the compressor 10 are connected by a return pipe provided with a pump 98 . For example, a pump with a flow rate of 0.1 L/min can be used for a 10 hp air conditioner. The separated split oil pressure is then raised by pump 98 , causing the split oil to flow to compressor 10 . However, if the above-mentioned method is used, the pump 98 needs to be additionally provided, and there is a problem that the cost of the air conditioner increases. In addition, the cooling power consumption or the heating power consumption increases due to the power consumption of the pump.

(3) As shown in FIG. 3 , in Background Art 3, on the oil return pipe connecting the oil separator 20 and the compressor 10 , the first check valve 51 , the oil accumulator 30 , the first check valve 51 , the oil accumulator 30 , the first check valve 51 , the Two one-way valves 52 . When the air conditioner is in cooling or heating operation, changes in room temperature, changes in the set air volume of indoor units, and changes in the number of indoor units operating in a multi-connection scenario will cause the discharge pressure of the compressor 10 to fluctuate repeatedly.

At this time, when the exhaust pressure rises, the first check valve 51 is opened, the second check valve 52 is closed, and the oil separated by the oil separator is moved to the oil accumulator and stored. When the discharge pressure drops, the first check valve is closed 51 , and then the second check valve 52 is opened, and the separated oil in the oil accumulator 30 moves to the compressor 10 .

However, in this method, when the compressor 10 is started, the discharge pressure rises, and it is not possible to move the oil from the oil accumulator 30 to the compressor when the discharge pressure drops. Therefore, the separated oil separated by the oil separator 20 will be stored in the oil accumulator 30. Since the pressure of the oil accumulator 30 is always lower than the discharge pressure of the compressor 10 at this stage, the oil separated by the oil separator 20 Failure to return to the compressor 10 may result in insufficient oil in the compressor 10.

In addition, when the indoor load fluctuation is small, for example, at noon time, the exhaust pressure change is small. Therefore, the oil in the oil separator cannot return to the compressor, which may also lead to insufficient oil in the compressor 10 .

Utility model content

The first object of the present invention is to provide a refrigerant compression device to solve the technical problem that the oil separator of the existing refrigerant compression device is not easy to return oil.

The refrigerant compression device provided by the utility model includes a compressor and an oil separator, the air outlet of the compressor is connected to the inlet of the oil separator through a first pipeline, and the oil separator has a first oil outlet, so The first oil outlet is communicated with the suction pipe of the compressor through a second pipeline, and an active control valve is arranged on the second pipeline.

By arranging an active control valve in the second line connecting the oil separator and the suction line of the compressor, the oil separated in the oil separator is spontaneously returned to the compressor by utilizing the fluctuation of the discharge pressure of the compressor. When the solution of the compressor cannot automatically return the oil, the active control valve is opened, so that the separated oil of the oil separator flows from the second pipeline to the suction pipe of the compressor. As long as the compressor is on, the pressure of the suction pipe of the compressor must be significantly lower than the discharge pressure of the compressor, so that the separated oil in the oil separator can be returned to the compressor, and the oil in the compressor can be replenished in time. , to avoid long-term oil shortage of the compressor.

In a preferred technical solution, a third pipeline is further included, the oil separator further has a second oil outlet, the second oil outlet is connected to the oil reservoir through a third pipeline, and the third pipeline is provided with a first oil outlet. A one-way valve, the oil accumulator is connected to the oil return port of the compressor through a fourth pipeline, and the first one-way valve can only conduct one-way conduction from the oil separator to the oil accumulator.

By arranging the third pipeline to be connected to the oil accumulator, and arranging the first check valve on the third pipeline, when the exhaust pressure of the compressor rises, the pressure of the oil separator is greater than the pressure of the oil accumulator, and the pressure of the oil separator is higher than that of the oil accumulator. Oil is recovered to the oil reservoir. Moreover, as long as there is a corresponding relationship between the pressures, the separated oil can flow into the oil reservoir without going through the detection and control links, and the operation reliability is high. In addition, even if the discharge pressure of the compressor is reduced, the pressure in the oil separator is lower than the pressure in the oil accumulator, the separated oil in the oil accumulator will not return to the oil due to the one-way conduction effect of the first check valve in the separator.

In a preferred technical solution, a second one-way valve is provided on the fourth pipeline, and the second one-way valve can only conduct one-way conduction from the oil accumulator to the compressor.

By arranging the second check valve on the fourth pipeline, when the discharge pressure of the compressor drops, the pressure of the oil accumulator is greater than the discharge pressure of the compressor, and the separated oil in the oil accumulator is spontaneously returned to the compressor . Moreover, as long as the above-mentioned corresponding relationship occurs in the pressure, the separated oil can flow into the compressor without going through the detection and control links, and the operation reliability is high.

In a preferred technical solution, a temperature sensor is provided on the fourth pipeline, and the temperature sensor is located between the second one-way valve and the oil return port of the compressor.

By setting a temperature sensor, the temperature of the separated oil returning from the oil accumulator to the compressor can be detected, and the temperature change of the oil accumulator can be known in time, so as to control the active control valve to perform corresponding actions, so that the separated oil from the oil accumulator can be used. The relative relationship between the temperature and the discharge temperature of the compressor determines whether the separated oil in the oil reservoir is in a flowing state.

In a preferred technical solution, a controller is also included, the active control valve is a solenoid valve, the active control valve is electrically connected to the controller, and the active control valve is used to disconnect under the control of the controller or conducting the second pipeline.

Using a solenoid valve electrically connected to the controller to disconnect or conduct the second pipeline under the control of the controller is beneficial to improve the response speed and achieve more precise control.

In a preferred technical solution, the controller is electrically connected to the temperature sensor, and the controller is used to obtain the return oil temperature detected by the temperature sensor.

By electrically connecting the controller and the temperature sensor to obtain the oil return temperature of the oil reservoir detected by the temperature sensor, the oil storage time of the oil reservoir can be reflected, so as to control the corresponding active control valve to operate.

In a preferred technical solution, the active control valve is configured to conduct when the temperature difference between the oil return temperature and the exhaust temperature of the compressor is greater than or equal to a first preset temperature difference within a first preset time period the second pipeline; and/or, the active control valve is configured to conduct the first pipeline when the fluctuation value of the discharge pressure of the compressor is smaller than the preset fluctuation value within the first preset time period .

When the difference between the return oil temperature and the exhaust gas temperature of the compressor is large within the first preset time period, it means that the separated oil of the oil separator is stored in the oil accumulator for a long time, and the separated oil dissipates more heat into the environment, so the temperature is higher than that of the oil separator. If it is low, it means that the compressor has been working for a long time in the state of relatively small oil volume. At this time, the active control valve can conduct the third pipeline under the control of the controller. Since the suction port pressure of the compressor is much smaller than the compressor discharge pressure, the pressure difference between the two is relatively large, so the separated oil is quickly added to the compressor to ensure the normal working state of the compressor.

And/or, it is also possible to detect the fluctuation value of the discharge pressure of the compressor. If the fluctuation value of the discharge pressure of the compressor is small, it means that it is difficult to use the pressure change between the compressor and the oil accumulator to pass the first check valve and the second check valve. The self-separated oil returns to the valve, and the active control valve can be actively opened at this time to return the oil to ensure the normal working state of the compressor.

In a preferred technical solution, a capillary is also provided on the second pipeline.

By setting the capillary, it can play a certain throttling effect, so as to avoid the high temperature of the separated oil returning to the suction pipe of the compressor, which will increase the exhaust temperature of the compressor, and reduce the reliability of the compressor.

The second object of the present invention is to provide an air conditioner outdoor unit to solve the technical problem that the oil separator of the refrigerant compression device of the existing air conditioner outdoor unit is not easy to return oil.

The air conditioner outdoor unit provided by the utility model includes the above-mentioned refrigerant compression device.

By arranging the above refrigerant compressing device in the outdoor unit of the air conditioner, correspondingly, the outdoor unit of the air conditioner has all the advantages of the above refrigerant compressing device, which will not be repeated here.

The third object of the present invention is to provide an air conditioner to solve the technical problem that the oil separator of the refrigerant compression device of the existing air conditioner outdoor unit is not easy to return oil.

The air conditioner provided by the utility model includes the above-mentioned outdoor unit of the air conditioner.

By arranging the above air conditioner outdoor unit in the air conditioner, correspondingly, the air conditioner has all the advantages of the above air conditioner outdoor unit, which will not be repeated here.

Description of drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the following briefly introduces the accompanying drawings that need to be used in the description of the embodiments or the prior art. Obviously, the accompanying drawings in the following description It is only an embodiment of the present invention, and for those of ordinary skill in the art, other drawings can also be obtained according to the provided drawings without creative efforts.

1 is a schematic structural diagram of background technology 1 in the background technology of the present invention;

2 is a schematic structural diagram of background technology 2 in the background technology of the present utility model;

3 is a schematic structural diagram of background technology 3 in the background technology of the present invention;

4 is a schematic structural diagram of a refrigerant compression device provided by an embodiment of the present invention;

5 is a schematic diagram of the state of the above-mentioned refrigerant compression device when the separated oil flows from the oil separator to the oil reservoir;

6 is a schematic diagram of the state of the above-mentioned refrigerant compression device when the separated oil flows from the oil reservoir to the oil separator;

7 is a schematic diagram of a work flow of the above-mentioned refrigerant compression device;

FIG. 8 is a schematic diagram of another working flow of the above-mentioned refrigerant compression device.

Description of reference numbers:

10-compressor; 20-oil separator; 30-oil accumulator; 40-active control valve; 51-first check valve; 52-second check valve; 60-temperature sensor; 71-first pipeline 72-second pipeline; 73-third pipeline; 74-fourth pipeline; 80-suction pipe; 98-pump; 99-capillary.

Detailed ways

In order to make the above objects, features and advantages of the present utility model more clearly understood, the specific embodiments of the present utility model are described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to explain the present invention, and are not intended to limit the present invention.

4 is a schematic structural diagram of a refrigerant compression device provided by an embodiment of the present invention. As shown in FIG. 4 , the refrigerant compression device provided in this embodiment includes a compressor 10 and an oil separator 20. The air outlet of the compressor 10 is connected to the inlet of the oil separator 20 through a first pipeline 71. The oil separator 20 has The first oil outlet is communicated with the suction pipe 80 of the compressor 10 through the second pipeline 72, and the second pipeline 72 is provided with an active control valve 40.

Specifically, the active control valve 40 may include an electric or manual or hydraulically controlled shut-off valve, a two-position two-way reversing valve, or a valve that can be opened and closed, such as an electronic expansion valve, although its main function is to Adjust the opening, but when the opening is adjusted to 0, it can be considered that the valve has cut off the pipeline where it is located. Or, when the four-way valve is in the position of being able to cut off or conduct a certain pipeline, it will not cause changes in other pipelines during the state change, that is, using a four-way valve as a two-position two-way valve can also be used as a two-way valve. The above-described active control valve 40 . Among them, a valve such as a one-way valve, which only depends on the relative pressure state of the external pipeline, determines whether the one-way valve conducts along the inlet end to the outlet end, does not belong to the above-mentioned active control valve 40 .

By arranging the active control valve 40 in the second line 72 that communicates between the oil separator 20 and the suction pipe 80 of the compressor 10 , the oil separator 20 is automatically moved to the oil separator 20 by utilizing the fluctuation of the discharge pressure of the compressor 10 . When the method of returning the separated oil to the compressor 10 cannot automatically return the oil, the active control valve 40 is opened to allow the separated oil of the oil separator 20 to flow from the second pipeline 72 to the suction pipe 80 of the compressor 10 middle. As long as the compressor 10 is in the open state, the pressure of the suction pipe 80 of the compressor 10 must be significantly lower than the discharge pressure of the compressor 10, so that the separated oil in the oil separator 20 can be returned to the compressor 10 and replenished in time. The amount of oil in the compressor 10 to prevent the compressor 10 from being short of oil for a long time.

As shown in FIG. 4 , preferably, a third pipeline 73 is further included, and the oil separator 20 also has a second oil outlet, and the second oil outlet is connected to the oil accumulator 30 through the third pipeline 73 . The first check valve 51 is provided, the oil accumulator 30 is connected to the oil return port of the compressor 10 through the fourth pipeline 74 , and the first check valve 51 can only conduct one-way conduction from the oil separator 20 to the oil accumulator 30 .

By arranging the third pipeline 73 to be connected to the oil accumulator 30 and arranging the first check valve 51 on the third pipeline 73, when the discharge pressure of the compressor 10 rises, the pressure of the oil separator 20 can be higher than that of the oil separator 20. The pressure of the oil accumulator 30 recovers the oil in the oil accumulator 30 . Moreover, as long as there is a corresponding relationship between the pressures, the separated oil can flow into the oil accumulator 30 without going through the link of detection and control, and the operation reliability is high. The state at this time is shown in FIG. 5 . Furthermore, even if the discharge pressure of the compressor 10 decreases, the pressure in the oil separator 20 is lower than the pressure in the oil accumulator 30 , due to the one-way conduction effect of the first check valve 51 . , the separated oil in the oil accumulator 30 will not return to the oil separator 20 either.

As shown in FIG. 4 , preferably, the fourth pipeline 74 is provided with a second one-way valve 52, and the second one-way valve 52 can only conduct one-way conduction from the oil accumulator 30 to the compressor 10.

By arranging the second check valve 52 on the fourth pipeline 74, when the discharge pressure of the compressor 10 drops, the pressure of the oil accumulator 30 is greater than the discharge pressure of the compressor 10, and the oil in the oil accumulator 30 is separated. It returns to the compressor 10 spontaneously, and the state at this time is as shown in FIG. 6 . Moreover, as long as the above-mentioned corresponding relationship occurs in the pressure, the separated oil can flow into the compressor 10 without going through the link of detection and control, and the operation reliability is high.

By adopting the solution of disposing the first check valve 51 and the second check valve 52 at both ends of the oil accumulator 30 respectively, the spontaneous return of the separated oil from the separator can be realized by utilizing the exhaust pressure fluctuation of the compressor 10 . Compared with the scheme of offsetting the pressure by height, the space occupied can be reduced; compared with the scheme of pumping with a pump, the power consumption can be reduced; The oil solution improves the reliability of the compressor 10 .

As shown in FIG. 4 , preferably, a temperature sensor 60 is provided on the fourth pipeline 74 , and the temperature sensor 60 is located between the second one-way valve 52 and the oil return port of the compressor 10 .

Specifically, the temperature sensor 60 can be an electronic temperature sensor 60, which transmits the pressure information of the fourth pipeline 74 to the controller as an electrical signal, and the controller judges according to the temperature signal, and operates the relevant action mechanism to act. In addition, it may also be a non-electronic thermometer, which visually displays the temperature in the fourth pipeline 74 to the operator.

By setting the temperature sensor 60, the temperature of the separated oil returned from the oil accumulator 30 to the compressor 10 can be detected, and the temperature change of the oil accumulator 30 can be known in time, so as to control the active control valve 40 to perform corresponding actions, so that the storage The relative relationship between the temperature of the separated oil in the oil tank 30 and the temperature of the exhaust gas of the compressor 10 determines whether the separated oil in the oil accumulator 30 is in a flowing state.

As shown in FIG. 4, preferably, it also includes a controller (not shown in the figure), the active control valve 40 is a solenoid valve, the active control valve 40 is electrically connected with the controller, and the active control valve 40 is used for controlling the controller. Disconnect or conduct the second pipeline 72 at the bottom.

Using a solenoid valve electrically connected to the controller to disconnect or conduct the second pipeline 72 under the control of the controller is beneficial to improve the response speed and achieve more precise control.

In another implementation manner, the controller may not be provided, and correspondingly, the active control valve 40 may be a manual valve. The operator observes the temperature gauge, and compares it with a preset value according to the indication on the temperature gauge. When the difference from the preset value is large, the active control valve 40 is opened, so that the oil separator 20 separates the oil. Flow through the second line 72 to the suction line 80 of the compressor 10, or during the start-up phase of the compressor 10 or periods when the discharge pressure of the compressor 10 may fluctuate less, the active control valve 40 is opened for a period of time. Although it is not as fast as the electronic control method, when the volume of the oil accumulator 30 is large and the oil volume in the compressor 10 is allowed to drop greatly, it is not necessary to quickly switch the communication state of the first pipeline 71 in a short time. , is also an optional way.

As shown in FIG. 4 , preferably, the controller is electrically connected to the temperature sensor 60 , and the controller is used to obtain the return oil temperature detected by the temperature sensor 60 .

By electrically connecting the controller with the temperature sensor 60 to obtain the oil return temperature of the oil accumulator 30 detected by the temperature sensor 60 , the oil storage time of the oil accumulator 30 can be reflected, so as to control the corresponding active control valve 40 to operate.

As shown in FIG. 4 , preferably, the active control valve 40 is configured to conduct the first operation when the temperature difference between the oil return temperature and the exhaust temperature of the compressor 10 is greater than or equal to the first preset temperature difference within the first preset time period. The second pipeline 72; and/or the active control valve 40 is configured to conduct the first pipeline 71 when the fluctuation value of the discharge pressure of the compressor 10 is smaller than the preset fluctuation value within the first preset time period.

When the separated oil of the oil separator 20 is stored in the oil accumulator 30 for a long time, the separated oil dissipates more heat into the environment, so the temperature is lower. That is, the difference between the return oil temperature and the exhaust gas temperature of the compressor 10 within the first preset time period is relatively large, indicating that the compressor 10 operates for a long time in a state with a relatively small amount of oil. At this time, the active control valve 40 can The third pipeline 73 is conducted under the control of the controller. Since the suction port pressure of the compressor 10 is much smaller than the discharge pressure of the compressor 10, and the pressure difference between the two is relatively large, the separated oil is quickly added to the compressor 10 to ensure the normal working state of the compressor 10.

And/or, the fluctuation value of the exhaust pressure of the compressor 10 can also be detected. If the fluctuation value of the exhaust pressure of the compressor 10 is small, it means that it is difficult to use the pressure changes of the compressor 10 and the oil accumulator 30 to pass the first check valve. 51 and the second one-way valve 52 realize spontaneous return of the separated oil. At this time, the active control valve 40 can be actively opened to return the oil, so as to ensure the normal working state of the compressor 10.

As shown in FIG. 4 , preferably, a capillary 99 is further provided on the second pipeline 72 .

By arranging the capillary tube 99, a certain throttling effect can be achieved, thereby preventing the temperature of the separated oil returning to the suction pipe 80 of the compressor 10 from being too high and increasing the exhaust gas temperature of the compressor 10, thereby reducing the reliability of the compressor 10.

As shown in FIG. 7 , the operating principle of the embodiment without setting the temperature sensor is as follows:

Taking an outdoor unit with a power of 10hp as an example, the oil separated by the oil separator is about 0.1L/min. In the scenario where the separated oil is returned only through the third pipeline and the fourth pipeline, if the pressure difference between the inlet side and the outlet side of the first check valve and the second check valve is 0.01MPa, the flow coefficient of the check valve needs to be above 0.02.

The flow coefficient can be calculated according to the following formula:

Flow coefficient=0.022×oil flow rate [L/min]×{oil specific gravity/pressure difference [MPa]}×0.5

Assuming that the separated oil in the oil accumulator can move to the compressor body once every 5 minutes, a capacity of more than 0.5L is required.

In the scenario where the oil is separated by backflow only through the second pipeline, according to the empirical value of the test results, the size of the capillary is about 1.0 mm in inner diameter and 700 mm in length.

Since the compressor is started, the solenoid valve is opened for a second preset time period Tr. In this embodiment, generally speaking, the time from the compressor startup to the continuous rise of the exhaust pressure is generally not more than 20 minutes, and the second preset time period Tr may also be about 20 minutes. If the solenoid valve is open for 20 minutes, the solenoid valve can be closed. The separated oil can be returned to the compressor through the path of the first one-way valve, the oil accumulator, and the second one-way valve.

In addition, when the compressor is stopped after a period of time and then restarted, the solenoid valve may also be opened for a second preset time period Tr. In this case, generally speaking, the time required from the compressor shutdown to the pressure of each refrigerant pipeline is about 30 minutes. If it is restarted after shutdown, and the elapsed time exceeds 30 minutes, the solenoid valve can also be opened, so that the separated oil flows back from the capillary to the suction port of the compressor.

As shown in FIG. 8 , the operating principle of the embodiment with a temperature sensor is as follows:

Take the last shutdown of the compressor as the start time of the process.

After the compressor is stopped, the shutdown time Tcs starts to count to determine whether the compressor starts to run. If the compressor starts to run, the temperature measurement time Tr starts to count; if the compressor does not start to run, the shutdown time Tcs continues to be counted.

When the temperature measurement time Tr starts to count, the exhaust temperature Td of the compressor is detected (the detection of the exhaust temperature of the compressor belongs to the prior art, which is not repeated in this application), and the temperature Tor of the temperature sensor is detected to determine the two Whether the difference exceeds the first preset temperature difference. Among them, it should be noted that, since the separated oil in the fourth pipeline detected by the temperature sensor is the separated oil that has stayed in the oil accumulator, or has passed through the oil accumulator, the distance from the exhaust gas of the compressor It has been a while since the outlet came out, so the temperature Tor of the temperature sensor should be less than the discharge temperature Td of the compressor. The difference between the two refers to the absolute value of the difference between the two temperature values.

The first preset temperature difference may be set to 10°C. When the difference between the two is smaller than the first preset temperature difference, the timing of Tr can be restarted. If the difference between the two is greater than the first preset temperature difference, it is determined whether Tr has reached the first preset duration, for example, the first preset duration may be 5 minutes. If Tr does not reach the first preset duration, Tor and Td may continue to be detected, and the difference between the two may be determined. If Tr reaches the first preset time period, the solenoid valve is opened.

Then, the exhaust gas temperature Td is detected and the temperature sensor is used to detect the separated oil temperature Tor of the fourth pipeline, and it is determined whether the difference between the two exceeds the first preset temperature difference. If it is exceeded, the solenoid valve is kept open and the detection is continued. If the difference between the two is less than the first preset temperature difference, it is likely that the separated oil in the oil accumulator starts to flow back to the compressor through the fourth pipeline, the solenoid valve is closed, and the process ends.

In addition, when the fluctuation of the indoor load is small, such as at noon time, even if the discharge pressure of the compressor does not fluctuate greatly, oil separation cannot be achieved by using the flow paths of the first check valve, the oil accumulator, and the second check valve. To prevent the return of oil from the compressor to the compressor, the separated oil can also be returned to the suction port of the compressor through the open solenoid valve and capillary to prevent insufficient oil in the compressor.

To sum up, the utility model has the following advantages:

1. When the separated oil of the oil separator returns to the compressor body, it will not cause the exhaust refrigerant to move to the compressor suction pipe through the oil return pipe. Therefore, it will not cause a decrease in the refrigerant flow rate of the indoor unit and cause a decrease in cooling capacity or heating capacity.

2. When the separated oil of the oil separator returns to the compressor body, the phenomenon that the high-temperature exhaust refrigerant is mixed into the suction refrigerant will not occur. Therefore, it will not cause the temperature of the exhaust gas to rise, causing the problem of reducing the reliability of the compressor.

3. There is no need to use a pump, which will not cause an increase in the manufacturing cost of the air conditioner, and can also prevent the increase of cooling power consumption or heating power consumption.

4. When the compressor starts, even if the oil cannot be moved from the oil separator to the compressor through the oil accumulator, the solenoid valve can be moved from the oil separator to the compressor. Therefore, the oil shortage problem in the compressor startup phase can be prevented.

5. Under normal conditions, the exhaust pressure fluctuation of the compressor can be used normally, and the oil is returned to the compressor from the first one-way valve, the oil accumulator and the second one-way valve. The second oil return pipe is not used when it is not necessary, so it can prevent the reliability of the compressor from decreasing due to the decrease of cooling capacity or heating capacity, or the increase of discharge temperature.

The present invention also provides an embodiment. The outdoor unit of the air conditioner provided by the embodiment includes the above-mentioned refrigerant compression device.

By arranging the above refrigerant compressing device in the outdoor unit of the air conditioner, correspondingly, the outdoor unit of the air conditioner has all the advantages of the above refrigerant compressing device, which will not be repeated here.

The present invention also provides an embodiment. The air conditioner provided by this embodiment includes the above-mentioned outdoor unit of the air conditioner.

By arranging the above air conditioner outdoor unit in the air conditioner, correspondingly, the air conditioner has all the advantages of the above air conditioner outdoor unit, which will not be repeated here.

Although the present invention is disclosed above, the present invention is not limited thereto. Any person skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, the protection scope of the present invention should be based on the scope defined by the claims.

Finally, it should also be noted that in this document, relational terms such as first and second are used only to distinguish one entity or operation from another, and do not necessarily require or imply these entities or that there is any such actual relationship or sequence between operations. Moreover, the terms "comprising", "comprising" or any other variation thereof are intended to encompass non-exclusive inclusion such that a process, method, article or device comprising a list of elements includes not only those elements, but also includes not explicitly listed or other elements inherent to such a process, method, article or apparatus. Without further limitation, an element qualified by the phrase "comprising a..." does not preclude the presence of additional identical elements in a process, method, article or apparatus that includes the element.

The various embodiments in this specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments, and the same and similar parts between the various embodiments can be referred to each other.

The above description of the disclosed embodiments enables those skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Thus, the present invention is not intended to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. The refrigerant compression device is characterized by comprising a compressor (10) and an oil separator (20), wherein an air outlet of the compressor (10) is connected with an inlet of the oil separator (20) through a first pipeline (71), the oil separator (20) is provided with a first oil outlet, the first oil outlet is communicated with an air suction pipe (80) of the compressor (10) through a second pipeline (72), and the second pipeline (72) is provided with a main control valve (40).

2. The refrigerant compression device according to claim 1, further comprising a third pipeline (73), wherein the oil separator (20) further has a second oil outlet, the second oil outlet is connected to an oil reservoir (30) through the third pipeline (73), a first check valve (51) is disposed on the third pipeline (73), the oil reservoir (30) is connected to an oil return port of the compressor (10) through a fourth pipeline (74), and the first check valve (51) can only conduct from the oil separator (20) to the oil reservoir (30) in one direction.

3. The refrigerant compression device as claimed in claim 2, wherein a second check valve (52) is provided on the fourth pipe (74), and the second check valve (52) is only capable of conducting from the oil reservoir (30) to the compressor (10) in one direction.

4. A refrigerant compression device as claimed in claim 3, wherein a temperature sensor (60) is provided on the fourth line (74), the temperature sensor (60) being located between the second check valve (52) and an oil return of the compressor (10).

5. The refrigerant compressing apparatus as claimed in claim 4, further comprising a controller, wherein the active control valve (40) is a solenoid valve, the active control valve (40) is electrically connected to the controller, and the active control valve (40) is used for disconnecting or connecting the second pipeline (72) under the control of the controller.

6. The refrigerant compressing device as claimed in claim 5, wherein the controller is electrically connected to the temperature sensor (60), and the controller is configured to obtain an oil return temperature detected by the temperature sensor (60).

7. The refrigerant compression device as claimed in claim 6, wherein the active control valve (40) is configured to conduct the second pipeline (72) when a temperature difference between the oil return temperature and the discharge temperature of the compressor (10) within a first predetermined time period is greater than or equal to a first predetermined temperature difference; and/or the active control valve (40) is used for conducting the second pipeline (72) when the fluctuation value of the discharge pressure of the compressor (10) in the first preset time period is smaller than the preset fluctuation value.

8. Refrigerant compression arrangement according to any of claims 1-7, characterised in that a capillary tube (99) is provided in the second line (72).

9. An outdoor unit of an air conditioner, comprising the refrigerant compression device as recited in any one of claims 1 to 8.

10. An air conditioner comprising the outdoor unit of claim 9.

Images