CN215724295U - Refrigerant compression device, air conditioner outdoor unit and air conditioner - Google Patents
Refrigerant compression device, air conditioner outdoor unit and air conditioner Download PDFInfo
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- CN215724295U CN215724295U CN202121876637.9U CN202121876637U CN215724295U CN 215724295 U CN215724295 U CN 215724295U CN 202121876637 U CN202121876637 U CN 202121876637U CN 215724295 U CN215724295 U CN 215724295U
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Abstract
The utility model relates to a refrigerant compression device, an air conditioner outdoor unit and an air conditioner, belongs to the technical field of air conditioners, and aims to solve the technical problem that an existing refrigerant compression device is not easy to return oil. The refrigerant compression device comprises a compressor and an oil separator, an air outlet of the compressor is connected with an inlet of the oil separator through a first pipeline, an oil outlet of the oil separator is connected with an oil storage device through a second pipeline, a first active control valve is arranged on the second pipeline, and the oil storage device is connected with an oil return port of the compressor through a third pipeline. The refrigerant compression device, the air conditioner outdoor unit and the air conditioner can open the first active control valve when the discharge pressure of the compressor is increased and is higher than a first preset pressure value, so that the refrigerant separated from the oil separator can spontaneously flow into the oil reservoir. When the discharge pressure is reduced and is lower than a first preset pressure value, the first active control valve can be closed, the pressure of the oil reservoir is higher than the discharge pressure, and the refrigerant can flow into an oil return port of the compressor.
Description
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
In an air conditioner, in order to prevent liquid in a refrigerant from flowing outward when an outdoor unit discharges air, an oil separator is provided in an exhaust pipe, and oil separated by the oil separator (hereinafter, referred to as separated oil) is returned to a compressor. However, when the compressor mounted on the air conditioner is a high-pressure compressor having a compressor body pressure equal to the discharge pressure, the pressure in the oil separator is lower than the compressor body pressure due to the discharge pipe pressure loss. Therefore, if only an 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 schemes are adopted in the prior art:
(1) as shown in fig. 1, in the conventional art 1, an oil separator and an intake pipe 80 of a compressor 10 are connected by a return oil pipe provided with a capillary tube 99, and for example, a capillary tube 99 having an inner diameter of 1.0mm and a length of 700mm can be used for a 10hp air conditioner. With the above configuration, the separated liquid refrigerant flows from the oil separator 20 to the suction pipe 80 of the compressor 10 having a low pressure, and then returns to the compressor 10. However, in this method, the gaseous portion of the exhaust refrigerant also flows to the suction pipe 80 through the return pipe. This reduces the flow rate of the refrigerant flowing into the indoor unit, and eventually deteriorates the cooling capacity or the heating capacity. Meanwhile, when a high-temperature exhaust refrigerant is mixed into the intake refrigerant, the intake temperature increases, which causes an increase in the exhaust temperature, and eventually, the reliability of the compressor 10 is also degraded.
(2) As shown in fig. 2, in prior art 2, the oil separator 20 is disposed at a higher position than the compressor 10, and the oil separator 20 and the compressor 10 are connected by a return pipe. Under the action of the water head pressure, the pressure of the separated liquid refrigerant in the return pipe is increased, so that the separated liquid refrigerant can return to the compressor 10. However, in this case, the pressure loss due to the increase in the length of the discharge pipe in the oil separator 20 is smaller than the pressure in the compressor main body equal to the discharge pressure. In the sense that the power of the compressor 10 is wasted.
Furthermore, in this method, the oil separator 20 must be installed at a high position where the head pressure of the liquid refrigerant separated by the return pipe is greater than the pressure difference between the oil separator 20 and the compressor body. For example, when the pressure difference between the oil separator 20 and the compressor main body is 0.02MPa, the density of the liquid refrigerant is 0.95g/cm3The oil separator 20 needs to be installed at a position 2.1m higher than the compressor 10. This causes a problem that the air conditioner needs to be large-sized.
Further, the oil separator 20 and the connection pipe of the oil separator 20 deteriorate the cooling capacity or the heating capacity of the air conditioner due to the duct resistance of the outdoor heat exchanger.
(3) As shown in fig. 3, in the prior art 3, the oil separator 20 and the compressor 10 are connected by a return pipe provided with a pump 98, and for example, for a 10hp air conditioner, a pump with a flow rate of 0.1L/min can be used. The separated liquid refrigerant is then pressurized by pump 98 to flow to compressor 10. However, the above method requires an additional pump 98, which causes a problem of an increase in the cost of the air conditioner. Further, the power consumption of the pump increases, resulting in an increase in cooling power consumption and heating power consumption.
Disclosure of Invention
The first objective of the present invention is to provide a refrigerant compressing device to solve the technical problem that the oil separator of the existing refrigerant compressing device is not easy to return oil.
The refrigerant compression device provided by the utility model comprises a compressor and an oil separator, wherein an air outlet of the compressor is connected with an inlet of the oil separator through a first pipeline, an oil outlet of the oil separator is connected with an oil reservoir through a second pipeline, a first active control valve is arranged on the second pipeline, and the oil reservoir is connected with an oil return port of the compressor through a third pipeline.
By arranging the first active control valve, when the discharge pressure of the compressor is increased and is higher than a first preset pressure value, the first active control valve is opened, so that the refrigerant separated from the oil separator can spontaneously flow from the oil separator to the oil reservoir along the second pipeline. When the discharge pressure of the compressor is reduced and is lower than a first preset pressure value, the first active control valve can be closed, the pressure in the oil reservoir is higher than the discharge pressure of the compressor, and the refrigerant in the oil reservoir can flow from the oil reservoir to an oil return port of the compressor through a third pipeline. Therefore, oil return of the oil separator of the refrigerant compression device can be realized, and compared with a scheme of offsetting pressure through height, the oil separator can reduce occupied space; compared with a scheme of pumping liquid refrigerant by using a pump, the power consumption can be reduced; compared with the scheme of utilizing the capillary tube to return oil to the air inlet of the compressor, the reliability of the compressor is improved.
In a preferred technical scheme, a second active control valve is arranged on the third pipeline.
By arranging the second active control valve on the third pipeline, when the discharge pressure of the compressor is increased and exceeds the first preset pressure value, the second active control valve is closed to disconnect the third pipeline, so that the refrigerant cannot flow from the compressor to the oil reservoir in the third pipeline due to the increased pressure of the compressor, and the liquid refrigerant cannot flow from the oil reservoir to the oil separator due to the fact that the pressure in the oil reservoir is larger than the pressure of the oil separator. When the discharge pressure of the compressor is lower than the first preset pressure value, the second active control valve can be opened, so that the third pipeline is conducted, and the liquid refrigerant in the oil storage device flows back to the oil return port of the compressor by utilizing the fact that the pressure in the oil storage device is higher than the discharge pressure of the compressor.
In a preferred technical scheme, a pressure sensor is arranged on the first pipeline.
By arranging the pressure sensor, the discharge pressure of the compressor can be known so as to control the first active control valve and/or the second active control valve to perform corresponding operation, so that the liquid refrigerant separated by the oil separator can spontaneously flow back to the compressor by utilizing the relative pressure between the oil separator and the oil reservoir or the relative pressure between the oil reservoir and the discharge pressure of the compressor.
In a preferred technical solution, the control system further comprises a controller, the first active control valve is a first electromagnetic valve, the first active control valve is electrically connected with the controller, and the first active control valve is used for disconnecting or connecting the second pipeline under the control of the controller.
The second loop is disconnected or connected under the control of the controller by utilizing the first electromagnetic valve electrically connected with the controller, so that the reaction speed is favorably improved, and more accurate control is realized.
In a preferred technical solution, the second active control valve is a second solenoid valve, the second active control valve is electrically connected to the controller, and the second active control valve is used for disconnecting or connecting the third pipeline under the control of the controller.
And the third loop is disconnected or connected under the control of the controller by utilizing the second electromagnetic valve electrically connected with the controller, so that the reaction speed is favorably improved, and more accurate control is realized.
In a preferred technical solution, the controller is configured to obtain a discharge pressure of the compressor detected by the pressure sensor.
The controller is electrically connected with the pressure sensor to acquire the exhaust pressure of the compressor detected by the pressure sensor, so that the change of the exhaust pressure of the compressor can be known in time, and the corresponding first electromagnetic valve and the corresponding second electromagnetic valve are controlled to operate.
In a preferred technical scheme, the first active control valve is used for conducting the second pipeline when the exhaust pressure exceeds a first preset pressure value within a first preset time period; the first active control valve is also used for disconnecting the second pipeline when the exhaust pressure is less than or equal to the first preset pressure value in the first preset duration;
the second active control valve is used for conducting the third pipeline when the exhaust pressure is reduced to be lower than a second preset pressure value within a second preset time period after the first active control valve is disconnected; the second active control valve is also used for disconnecting the third pipeline when the exhaust pressure is still higher than the second preset pressure value after the first active control valve is disconnected and the second preset time period is reached.
The first active control valve is connected with the second pipeline when the exhaust pressure is greater than the first preset pressure value, and the second pipeline is disconnected when the exhaust pressure is less than the first preset pressure value, so that the separated liquid refrigerant can automatically flow into the oil reservoir by utilizing the pressure difference when the pressure of the oil separator is greater than that of the oil reservoir. And when the exhaust pressure of the second active control valve is reduced to be lower than a second preset pressure value, the third pipeline is conducted, and when the exhaust pressure is still higher than the second preset pressure value, the third pipeline can be disconnected. When the pressure of the oil storage device is larger than the exhaust pressure of the compressor, the separated liquid refrigerant can automatically flow into the oil storage device by utilizing the pressure difference. Therefore, the automatic flowing of the liquid refrigerant back to the oil return port of the compressor is finally realized.
In a preferred technical scheme, the first active control valve is used for conducting the second pipeline when the first active control valve and the second active control valve are not opened within a third preset time period; the compressor is used for increasing the rotating speed when the first active control valve and the second active control valve are not opened within a third preset time period; the first active control valve is used for disconnecting the second pipeline after a fourth preset time, the second active control valve is used for connecting the third pipeline after the fourth preset time, and the compressor is used for reducing the rotating speed after the fourth preset time; and the second electromagnetic valve is used for disconnecting the third pipeline after a fifth preset time period.
When the first active control valve and the second active control valve are not opened within the first preset time period, the fact that the discharge pressure of the compressor is not enough to enable the liquid refrigerant in the oil separator to flow into the oil reservoir is indicated, and therefore the rotating speed of the compressor is increased and the first active control valve is opened. When the first active control valve is opened for a third preset time, the first active exhaust control valve is conducted to the second pipeline, the second active control valve is disconnected from the third pipeline, the rotating speed of the compressor is reduced, the exhaust pressure of the compressor is reduced, the pressure of the outlet end of the second active control valve is reduced, and therefore the pressure in the oil storage device is greater than the pressure of the outlet end of the second active control valve, and liquid refrigerant in the oil storage device flows back to an oil return port of the compressor through the third pipeline.
A second object of the present invention is to provide an outdoor unit of an air conditioner, so as to solve the technical problem that an oil separator of a refrigerant compression device of an existing outdoor unit of an air conditioner is not easy to return oil.
The utility model provides an air conditioner outdoor unit, which comprises the refrigerant compression device.
By arranging the refrigerant compression device in the air conditioner outdoor unit, the air conditioner outdoor unit has all the advantages of the refrigerant compression device, and the description is omitted.
A third object of the present invention is to provide an air conditioner, which solves the technical problem that an oil separator of a refrigerant compression device of an outdoor unit of an air conditioner is not easy to return oil.
The air conditioner provided by the utility model comprises the air conditioner outdoor unit.
By arranging the air conditioner outdoor unit in the air conditioner, the air conditioner has all the advantages of the air conditioner outdoor unit, and the description is omitted.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
Fig. 1 is a schematic structural diagram of prior art 1 in the background of the utility model;
FIG. 2 is a schematic structural diagram of prior art 2 in the background of the utility model; (ii) a
FIG. 3 is a schematic diagram of a prior art 3 in the background of the utility model;
fig. 4 is a schematic structural diagram of a refrigerant compression device according to an embodiment of the present invention;
fig. 5 is a schematic view illustrating a state of the refrigerant compression device when the liquid refrigerant flows from the oil separator to the oil reservoir;
fig. 6 is a schematic view illustrating a state of the refrigerant compression device when the liquid refrigerant flows from the oil reservoir to the oil separator;
fig. 7 is a schematic view of a working process of the refrigerant compressing device;
fig. 8 is a schematic view of another operation flow of the refrigerant compression device.
Description of reference numerals:
10-a compressor; 20-an oil separator; 30-an oil reservoir; 40-a first active control valve; 50-a second active control valve; 60-a pressure sensor; 71-a first conduit; 72-a second conduit; 73-a third line; 80-suction pipe; 98-a pump; 99-capillary.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.
Fig. 4 is a schematic structural diagram of a refrigerant compression device according to an embodiment of the present invention. As shown in fig. 4, the refrigerant compressing apparatus according to the present embodiment includes a compressor 10 and an oil separator 20, an air outlet of the compressor 10 is connected to an inlet of the oil separator 20 through a first pipeline 71, an oil outlet of the oil separator 20 is connected to an oil reservoir 30 through a second pipeline 72, the second pipeline 72 is provided with a first active control valve 40, and the oil reservoir 30 is connected to an oil return port of the compressor 10 through a third pipeline 73.
Specifically, the first active control valve 40 may include an electric or manual or hydraulic control stop valve, a two-position two-way directional valve, or a valve that can adjust the opening degree and can be closed, such as an electronic expansion valve, and although its main function is to adjust the opening degree, when the opening degree is adjusted to 0, the valve may be considered to block the pipeline in which it is located. Alternatively, when the four-way valve is in a state where a certain line can be cut off or turned on without causing a change in the other lines during a state change, that is, one four-way valve is used as a two-position two-way valve, it may be used as the first active control valve 40. The valve, such as a check valve, in which whether the check valve conducts from the inlet end to the outlet end is determined only by the relative pressure state of the external pipe, does not belong to the first active control valve 40 described above.
By providing the first active control valve 40, it is possible to open the first active control valve 40 when the discharge pressure of the compressor 10 is increased to be higher than the first preset pressure value, so that the refrigerant separated in the oil separator 20 can spontaneously flow from the oil separator 20 to the oil reservoir 30 along the second line 72. When the discharge pressure of the compressor 10 is decreased to be lower than the first preset pressure value, the first active control valve 40 may be closed, the pressure in the oil reservoir 30 is higher than the discharge pressure of the compressor 10, and the refrigerant in the oil reservoir 30 may flow from the oil reservoir 30 to the oil return port of the compressor 10 through the third line 73. Thus, oil return of the oil separator 20 of the refrigerant compression device can be achieved, and the occupied space can be reduced compared with a scheme of offsetting pressure through the height; power consumption may be reduced compared to a scheme using a pump for pumping; the reliability of the compressor 10 is improved compared to a scheme in which oil is returned to the air inlet of the compressor 10 by a capillary tube.
As shown in fig. 4, the third line 73 is preferably provided with a second active control valve 50.
The kind of the valve selected by the second active control valve 50 may be the same as that of the valve selected by the first active control valve 40, and reference is made to the description of the first active control valve 40, which is not repeated herein.
By providing the second active control valve 50 on the third pipeline 73, when the discharge pressure of the compressor 10 increases and exceeds the first preset pressure value, the second active control valve 50 is closed to disconnect the third pipeline 73, so that the increased pressure of the compressor 10 does not cause the refrigerant to flow from the compressor 10 to the oil reservoir 30 in the third pipeline 73, and the pressure in the oil reservoir 30 is not greater than the pressure of the oil separator 20, so that the liquid refrigerant flows from the oil reservoir 30 to the oil separator 20. When the discharge pressure of the compressor 10 is lower than the first preset pressure value, the second active control valve 50 may be opened, so as to conduct the third pipeline 73, and the liquid refrigerant in the oil reservoir 30 is returned to the oil return port of the compressor 10 by using the pressure in the oil reservoir 30 being higher than the discharge pressure of the compressor 10.
As shown in fig. 4, the first pipe 71 is preferably provided with a pressure sensor 60.
Specifically, the pressure sensor 60 may be an electronic pressure sensor 60, and the pressure information of the first pipe 71 is transmitted to the controller as an electric signal, and the controller determines the pressure information based on the pressure signal and operates the relevant operation mechanism. In addition, a non-electronic pressure gauge may be used to visually display the pressure in the first pipeline 71 to the operator.
By providing the pressure sensor 60, the discharge pressure of the compressor 10 can be known to control the first active control valve 40 and/or the second active control valve 50 to operate accordingly, so that the liquid refrigerant separated by the oil separator 20 can be spontaneously returned to the compressor 10 by using the relative pressure between the oil separator 20 and the oil reservoir 30 or the relative pressure between the oil reservoir 30 and the discharge pressure of the compressor 10.
Preferably, a controller (not shown) is further included, the first active control valve 40 is a first solenoid valve, the first active control valve 40 is electrically connected to the controller, and the first active control valve 40 is used for disconnecting or connecting the second pipeline 72 under the control of the controller.
The second loop is disconnected or connected under the control of the controller by utilizing the first electromagnetic valve electrically connected with the controller, so that the reaction speed is favorably improved, and more accurate control is realized.
In other implementations, no controller may be provided, and accordingly, the first and second active control valves 40 and 50 may be manual valves. An operator observes the pressure gauge, compares the indication number on the pressure gauge with a preset numerical value, opens the first active control valve 40 and closes the second active control valve 50 when the indication number is larger than the preset numerical value and the exhaust pressure is in an ascending stage, so that the liquid refrigerant in the oil separator 20 flows into the oil reservoir 30, closes the first active control valve 40 and opens the second active control valve 50 when the indication number is smaller than the preset numerical value and the exhaust pressure is in a descending stage, so that the liquid refrigerant in the oil reservoir 30 flows into an oil return port of the compressor 10. Although not as rapid as an electronically controlled approach, it is also an alternative in situations where the communication state of the reservoir 30 does not need to be rapidly switched in a short time when the volume of the reservoir 30 is large.
Preferably, the second active control valve 50 is a second solenoid valve, the second active control valve 50 is electrically connected to the controller, and the second active control valve 50 is used for disconnecting or connecting the third pipeline 73 under the control of the controller.
And the third loop is disconnected or connected under the control of the controller by utilizing the second electromagnetic valve electrically connected with the controller, so that the reaction speed is favorably improved, and more accurate control is realized.
Preferably, the controller is configured to obtain the discharge pressure of the compressor 10 detected by the pressure sensor 60.
By electrically connecting the controller with the pressure sensor 60 to obtain the discharge pressure of the compressor 10 detected by the pressure sensor 60, the discharge pressure variation of the compressor 10 can be known in time, so as to control the corresponding first solenoid valve and second solenoid valve to operate.
Fig. 5 is a schematic view illustrating a state of the refrigerant compression device when the liquid refrigerant flows from the oil separator to the oil reservoir; fig. 6 is a schematic view of the refrigerant compression device in a state where the liquid refrigerant flows from the oil reservoir to the oil separator. As shown in fig. 5 and 6, preferably, the first actively controlled valve 40 is adapted to open the second line 72 when the exhaust pressure exceeds a first preset pressure value for a first preset period of time; the first active control valve 40 is also used for disconnecting the second pipeline 72 when the exhaust pressure is less than or equal to a first preset pressure value within a first preset time period;
the second active control valve 50 is used for conducting the third pipeline 73 when the exhaust pressure is reduced to be lower than a second preset pressure value within a second preset time period after the first active control valve 40 is disconnected; the second active control valve 50 is also adapted to disconnect the third line 73 when the exhaust pressure is still higher than the second preset pressure value for a second preset period of time after the first active control valve 40 is disconnected.
By making the first active control valve 40 conduct the second pipeline 72 when the discharge pressure is greater than the first preset pressure value and disconnecting the second pipeline 72 when the discharge pressure is less than the first preset pressure value, it can be realized that when the pressure of the oil separator 20 is greater than the pressure of the oil reservoir 30, the separated liquid refrigerant automatically flows into the oil reservoir 30 by using the pressure difference. So that the second active control valve 50 opens the third line 73 when the exhaust pressure drops below the second preset pressure value, and may open the third line 73 when the exhaust pressure is still higher than the second preset pressure value. It is possible to automatically flow the separated liquid refrigerant into the oil reservoir 30 by using the pressure difference when the pressure of the oil reservoir 30 is greater than the discharge pressure of the compressor 10. Thus, the automatic flow of the liquid refrigerant back to the oil return port of the compressor 10 is finally realized.
Preferably, the first active control valve 40 is used for conducting the second pipeline 72 when neither the first active control valve 40 nor the second active control valve 50 is opened within a third preset time period; the compressor 10 is used for increasing the rotation speed of the compressor 10 when the first active control valve 40 and the second active control valve 50 are not opened within a third preset time period; and the first active control is used for valve-breaking the second pipeline 72 after a fourth preset duration, the second active control valve 50 is used for conducting the third pipeline 73 after the fourth preset duration, and the compressor 10 is used for reducing the rotation speed after the fourth preset duration; and the second solenoid valve is used to disconnect the third pipeline 73 after a fifth preset period of time has elapsed.
When neither the first active control valve 40 nor the second active control valve 50 is opened for the first preset time period, it indicates that the discharge pressure of the compressor 10 is not enough to flow the liquid refrigerant in the oil separator 20 into the oil reservoir 30, so the rotation speed of the compressor 10 is increased and the first active control valve 40 is opened. With such a configuration, on the one hand, a decrease in the separation effect due to an excessive amount of liquid refrigerant in the oil separator 20 can be avoided, and on the other hand, an influence on the refrigeration effect due to an excessive amount of refrigerant in the compressor 10 can be prevented. After the first active control valve 40 is opened for a third preset time period, the first active exhaust control valve is connected to the second pipeline 72, the second active control valve 50 is disconnected from the third pipeline 73, the rotation speed of the compressor 10 is reduced, the exhaust pressure of the compressor 10 is reduced, the pressure at the outlet end of the second active control valve 50 is reduced, and accordingly, the pressure in the oil reservoir 30 is greater than the pressure at the outlet end of the second active control valve 50, and the liquid refrigerant in the oil reservoir 30 flows back to the oil return port of the compressor 10 through the third pipeline 73.
Fig. 7 is a schematic diagram of a working flow of the refrigerant compression device. As shown in fig. 7, the operation principle of the present embodiment is:
when the air conditioner is performing a cooling operation or a heating operation, the exhaust pressure repeatedly changes in the vertical direction when the indoor environment changes, the indoor set temperature changes, the indoor set air volume changes, or the number of indoor units operating in a scene of a plurality of indoor units changes.
First, the first and second active control valves 40 and 50 are closed when the compressor 10 starts to operate.
Then, when the discharge pressure of the compressor 10 rises above a first preset pressure value within a first preset discharge time period, the first active control valve 40 is opened; if not rising above the first preset pressure value for the first preset exhaust period, the first active control valve 40 is kept closed. Specifically, in this embodiment, the first preset discharge time period may be 5s, and the first preset pressure value may be obtained by adding an upper floating value to a nominal value of the operation of the compressor 10, for example, the nominal value of the discharge pressure of the operation of the compressor 10 is 3MPa, the upper floating value may be 0.01MPa, and the first preset pressure value may be 3.01 MPa. When the first active control valve 40 is opened for a long time, the first active control valve 40 may be closed, or the first active control valve 40 may be closed when the exhaust pressure starts to decrease.
Specifically, when the discharge pressure of the compressor 10 increases, the first active control valve 40 is opened, and the second active control valve 50 is closed, and the pressure relationship of each portion is as follows: in the compressor 10, the oil return pressure P of the compressor 10 on the outlet side of the second active control valve 502And the discharge pressure P of the compressor 101Equal; pressure P in the oil separator 20 on the inlet side of the first active control valve 403The pressure loss Δ Pdp of the first pipe 71 is smaller than the discharge pressure P of the compressor 101(ii) a And the outlet side of the first active control valve 40, i.e., the inlet side of the second active control valve 50, i.e., the pressure P in the oil reservoir 304With increasing exhaust pressure, P4Must fall behind P3Is increased. In summary, P1＝P2＞P3＞P4. Therefore, during the period when the discharge pressure is increased, the first active control valve 40 is opened and the second active control valve 50 is closed, and the liquid refrigerant in the oil separator 20 flows to the oil reservoir 30 through the first active control valve 40.
In order to facilitate control of the operation of the second active control valve 50, the actual pressure when the pressure does not rise above the first preset pressure value within the first preset exhaust period may be memorized as a memorized pressure value.
Then, when the discharge pressure is less than or equal to a second preset pressure value within a second preset time, the second active control valve 50 is opened to conduct the oil reservoir 30 and the oil return port of the compressor 10. When the exhaust pressure is still greater than the second preset pressure value at the second preset time, the second active control valve 50 is kept closed. Specifically, the second preset pressure value may be the memory pressure value minus the lower float value. Wherein, the second preset exhaust time can be 5s, and the lower floating value can be 0.01 MPa. Alternatively, the second predetermined pressure value may be a value previously stored in the memory, for example, a nominal value of 3MPa for the discharge pressure of the compressor 10, minus the lower float value of 0.01MPa, to 2.99 MPa. Further, the second active control valve 50 may be closed after being opened, or after a predetermined length of time has elapsed, which may be 5s, or 10s, or 20 s. After such a long time, it is considered that the liquid refrigerant in the accumulator 30 has completely flowed into the compressor 10 by the pressure difference.
Specifically, when the discharge pressure of the compressor 10 decreases, the first active control valve 40 is closed, and the second active control valve 50 is opened, and the pressure relationship at each position is as follows: in the compressor 10, the oil return pressure P of the compressor 102And the discharge pressure P of the compressor 101Equal; pressure P in the oil separator 20 on the inlet side of the first active control valve 403The pressure loss Δ Pdp of the first pipe 71 is smaller than the discharge pressure P of the compressor 101(ii) a And pressure P in the reservoir 304As the exhaust pressure decreases, the decrease in P4 necessarily lags behind P2Is reduced. In summary, P4＞P1＝P2＞P3. Therefore, if the first active control valve 40 is closed and the second active control valve 50 is opened during a period in which the discharge pressure is decreased, the liquid refrigerant in the accumulator 30 flows to the oil return port of the compressor 10 through the second active control valve 50.
Specifically, the operation process of the above operation principle is as follows:
1. taking the case that the discharge pressure is increased from 3.00MPa to 3.03MPa, when the discharge pressure is increased to a first preset pressure value of-3.01 MPa, the first active control valve 40 is opened, and the liquid refrigerant of the oil separator 20 flows into the oil reservoir 30 through the first active control valve 40. Since the second active control valve 50 is in the closed state, the liquid refrigerant is also retained in the accumulator 30.
2. Next, a description will be given of a scenario in which the exhaust pressure is stabilized at 3.03MPa for 5 seconds or more, then changes from 3.03MPa to 3.00MPa, and then decreases by 0.03 MPa: since the discharge pressure stabilization time lasts for 5s, the first active control valve 40 is closed, and then the stored discharge pressure is memorized as 3.03 MPa. When the discharge pressure is reduced to 3.02MPa, which is the second preset pressure value described above, the second active control valve 50 is opened. When the discharge pressure of the compressor 10 is reduced to 3.00MPa, the pressure of the oil return port of the compressor 10 is also reduced to 3.00 MPa. Assuming that the pressure loss of the first pipe 71 is 0.01MPa at this time, the pressure in the oil separator 20, i.e., the inlet-side pressure of the first active control valve 40, is reduced from 3.02MPa to 2.99 MPa. And the first active control valve 40 is in a closed state, the outlet side of the first active control valve 40, i.e., the pressure of the oil reservoir 30 is still 3.02 MPa. Therefore, the liquid refrigerant staying at the pressure of 3.02MPa flows into the compressor 10 at the pressure of 3.00MPa through the second active control valve 50. Through the above process, the liquid refrigerant staying in the accumulator 30 is returned to the compressor 10.
If the liquid refrigerant stays in the oil separator 20 and/or the oil reservoir 30, when the compressor 10 is stopped, the first and second active control valves 40 and 50 are opened, the pressure in the compressor 10 is lowered due to the pressure equalization of the refrigerant line of the air conditioner, and the liquid refrigerant in the oil separator 20 and/or the oil reservoir 30 automatically flows to the compressor 10. There is no concern that the liquid refrigerant may remain in the oil separator 20 or the oil reservoir 30 during a shutdown of the air conditioner, resulting in a lack of refrigerant when the compressor 10 is restarted.
Fig. 8 is a schematic view of another operation flow of the refrigerant compression device. In another operation flow, as shown in fig. 8, if neither the first and second active control valves 40 and 50 are opened for the third preset period of time, the first active control valve 40 is opened to increase the rotation speed of the compressor 10. Specifically, the third preset time is more than or equal to 5 minutes, and the rotating speed of the compressor 10 can be increased by 5%.
At this time, if the exhaust pressure rises to not less than 0.02MPa, the rotation speed of the compressor 10 is repeatedly increased by 5% until the exhaust pressure rises to 0.02 MPa. Through the above process, since the pressure in the oil separator 20 is greater than the pressure in the oil reservoir 30, for the specific reason that the pressure at each position during the exhaust pressure rising process can be analyzed as described above, the liquid refrigerant in the oil separator 20 flows into the oil reservoir 30.
Then, after the exhaust pressure has risen by 0.02MPa, the first active control valve 40 is opened again for a fourth predetermined period of time, the second line 72 is disconnected, and simultaneously the second active control valve 50 is opened, and the third line 73 is connected. At the same time, the rotation speed of the compressor 10 is reduced. Specifically, the fourth preset time period may be 20s, and the rotation speed of the compressor 10 may be reduced by 5%. If the decrease in the discharge pressure does not reach 0.02MPa or more, the operation of decreasing the rotation speed of the compressor 10 is repeated until the discharge pressure decreases to 0.02 MPa. At this time, since the pressure of the oil return port of the compressor 10 is lower than the pressure of the oil reservoir 30, for the reason that the pressure at each position during the discharge pressure drop can be analyzed as described above, the liquid refrigerant in the oil reservoir 30 flows to the oil return port of the compressor 10.
Then, after the second active control valve 50 is opened for a fifth preset period of time, the second active control valve 50 is closed, and the third line 73 is disconnected, so that the operation of the compressor 10 is restored to normal. Specifically, the fifth preset time period may be 20 s.
By adopting the above scheme, when the variation of the discharge pressure of the compressor 10 does not reach a degree enough to cause the variation of the first active control valve 40 and the second active control valve 50, the discharge pressure of the compressor 10 can be changed forcibly, and after the discharge pressure reaches the standard, the first active control valve 40 and the second active control valve 50 are controlled to perform corresponding actions, so that the liquid refrigerant in the oil separator 20 flows back to the oil return port of the compressor 10, on one hand, the reduction of the separation effect caused by excessive liquid refrigerant in the oil separator 20 can be avoided, and on the other hand, the influence of the refrigeration effect caused by too small refrigerant quantity in the compressor 10 can be prevented.
In addition, if a controller is not used to control the first and second active control valves 40 and 50, manual valves are used as the first and second active control valves 40 and 50. The operator can determine whether to open the corresponding valve based on the indication of the pressure gauge as the pressure sensor 60. For example, after the compressor 10 of the air conditioner starts to operate, the first and second active control valves 40 and 50 are closed. When the pressure gauge exceeds 3.01MPa, the first active control valve 40 is actively opened so that the liquid refrigerant flows from the oil separator 20 to the oil reservoir 30. The first actively controlled valve 40 may be closed when the reading of the pressure gauge is observed to be falling, or after a predetermined period of time, such as 20 seconds. The second active control valve 50 is then opened. When the discharge pressure is decreased, the liquid refrigerant in the oil reservoir 30 can flow back to the oil return port of the compressor 10.
In the embodiment described above, the liquid refrigerant in the oil separator 20 is returned to the compressor 10, so that there is no problem that the discharge refrigerant flows to the suction pipe of the compressor 10 through the oil return pipe. Therefore, there is no fear of deterioration of cooling capacity or heating capacity due to reduction of the amount of the circulating refrigerant, and there is no problem of reliability of the compressor 10 due to increase of discharge temperature since the high-temperature discharge refrigerant is not mixed into the suction refrigerant.
Further, this embodiment also does not require restrictions on the installation positions of the compressor 10 and the oil separator 20. Therefore, there is no need to worry about the problem of large-scale outdoor unit of air conditioner when using the prior art.
Further, this embodiment does not have the problem that the oil separator 20 and the oil separator 20 connecting pipe deteriorate in cooling capacity and heating capacity due to the duct resistance of the outdoor heat exchanger.
Since this proposal does not require the use of a pump, the cost increase of the air conditioner can be suppressed. While suppressing an increase in cooling power consumption or heating power consumption.
The utility model further provides an embodiment, which provides an air conditioner outdoor unit, comprising the refrigerant compression device.
By arranging the refrigerant compression device in the air conditioner outdoor unit, the air conditioner outdoor unit has all the advantages of the refrigerant compression device, and the description is omitted.
The utility model further provides an embodiment, and the air conditioner provided by the embodiment comprises the air conditioner outdoor unit.
By arranging the air conditioner outdoor unit in the air conditioner, the air conditioner has all the advantages of the air conditioner outdoor unit, and the description is omitted.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the utility model as defined in the appended claims.
Finally, it should also be noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make 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 applied to other embodiments without departing from the spirit or scope of the utility model. 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), an oil outlet of the oil separator (20) is connected with an oil reservoir (30) through a second pipeline (72), a first active control valve (40) is arranged on the second pipeline (72), and the oil reservoir (30) is connected with an oil return port of the compressor (10) through a third pipeline (73).
2. A refrigerant compression device as claimed in claim 1, wherein a second active control valve (50) is provided in the third line (73).
3. Refrigerant compression device as claimed in claim 2, characterised in that the first line (71) is provided with a pressure sensor (60).
4. A refrigerant compressing device as claimed in claim 3, further comprising a controller, wherein the first active control valve (40) is a first solenoid valve, the first active control valve (40) is electrically connected to the controller, and the first active control valve (40) is used for disconnecting or connecting the second pipeline (72) under the control of the controller.
5. A refrigerant compression device as claimed in claim 4, wherein the second active control valve (50) is a second solenoid valve, the second active control valve (50) is electrically connected to the controller, and the second active control valve (50) is adapted to open or close the third line (73) under the control of the controller.
6. The refrigerant compression device as claimed in claim 5, wherein the controller is configured to obtain a discharge pressure of the compressor (10) detected by the pressure sensor (60).
7. A refrigerant compression device as claimed in claim 6, wherein the first actively controlled valve (40) is adapted to open the second conduit (72) when the discharge pressure exceeds a first predetermined pressure value for a first predetermined period of time; the first active control valve (40) is also used for disconnecting the second pipeline (72) when the exhaust pressure is less than or equal to the first preset pressure value within the first preset time period;
the second active control valve (50) is used for conducting the third pipeline (73) when the exhaust pressure is reduced to be lower than the second preset pressure value within a second preset time period after the first active control valve (40) is disconnected; the second active control valve (50) is also used for disconnecting the third pipeline (73) when the exhaust pressure is still higher than the second preset pressure value after the first active control valve (40) is disconnected and the second preset time period is reached.
8. A refrigerant compression device as claimed in claim 6, wherein the first active control valve (40) is adapted to communicate with the second line (72) when neither the first active control valve (40) nor the second active control valve (50) is open for a third predetermined period of time; the compressor (10) is used for increasing the rotation speed of the compressor (10) when the first active control valve (40) and the second active control valve (50) are not opened within a third preset time period; and the first active control is used for switching off the second pipeline (72) after a fourth preset time period, the second active control valve (50) is used for switching on the third pipeline (73) after the fourth preset time period, and the compressor (10) is used for reducing the rotating speed after the fourth preset time period; and the second solenoid valve is used for disconnecting the third pipeline (73) after a fifth preset time period.
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.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121876637.9U CN215724295U (en) | 2021-08-11 | 2021-08-11 | Refrigerant compression device, air conditioner outdoor unit and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121876637.9U CN215724295U (en) | 2021-08-11 | 2021-08-11 | Refrigerant compression device, air conditioner outdoor unit and air conditioner |
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| CN215724295U true CN215724295U (en) | 2022-02-01 |
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| CN202121876637.9U Active CN215724295U (en) | 2021-08-11 | 2021-08-11 | Refrigerant compression device, air conditioner outdoor unit and air conditioner |
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Effective date of registration: 20221024 Address after: 315191 No. 1166 Mingguang North Road, Jiangshan Town, Ningbo, Zhejiang, Yinzhou District Patentee after: NINGBO AUX ELECTRIC Co.,Ltd. Patentee after: AUX AIR CONDITIONING LIMITED BY SHARE Ltd. Address before: 315191 No. 1166 Mingguang North Road, Jiangshan Town, Ningbo, Zhejiang, Yinzhou District Patentee before: NINGBO AUX ELECTRIC Co.,Ltd. Patentee before: Ningbo Oxfam intelligent commercial air conditioning manufacturing Co.,Ltd. |