CN110671833A

CN110671833A - Compressor and refrigerating system

Info

Publication number: CN110671833A
Application number: CN201810719401.0A
Authority: CN
Inventors: 廖四清; 杨宇飞; 王小龙; 王明然
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2018-07-03
Filing date: 2018-07-03
Publication date: 2020-01-10

Abstract

The invention discloses a compressor and a refrigerating system, wherein the compressor comprises: a housing having an accommodating chamber, a suction port, and a discharge port; the compression mechanism is arranged in the accommodating cavity and is provided with an air suction port and an air exhaust port, the air suction port is communicated with the suction port, and the air exhaust port is communicated with the accommodating cavity; the driving mechanism is in transmission connection with the compression mechanism; one end of the first flow control piece is communicated with the air suction port of the compression mechanism, the other end of the first flow control piece is communicated with the accommodating cavity, and the first flow control piece can be switched between the states of communicating and disconnecting the air suction port and the accommodating cavity; the second flow direction control piece is used for controlling the unidirectional circulation of the air flow along the suction inlet and the compression mechanism to the discharge outlet; and the wiring part is respectively connected with the driving mechanism and the first flow direction control part. The compressor has the advantages of high heat exchange efficiency and annual energy efficiency, small starting impact, convenient installation, good integrity and low cost.

Description

Compressor and refrigerating system

Technical Field

The invention relates to the technical field of compressors, in particular to a compressor and a refrigerating system with the same.

Background

The compressor adopted by the constant-speed air conditioning system runs at a constant speed, so that when the indoor heat load is less than the refrigerating capacity of the compressor, the compressor must be continuously started and stopped to maintain the constant indoor temperature, and the frequent starting and stopping of the compressor reduces the refrigerating efficiency of the air conditioning system under partial load, thereby reducing the annual energy efficiency.

Meanwhile, most of the existing air conditioning systems adopt capillary tubes, electronic expansion valves, thermal expansion valves and the like as throttling elements, and the throttling elements do not have the capacity of completely shutting down when the compressor is stopped. Therefore, when the compressor is just stopped, the refrigerant on the high-pressure side flows to the low-pressure side rapidly through the throttling element, so that the high-temperature refrigerant on the high-pressure side and the low-temperature refrigerant on the low-pressure side are rapidly mixed, and the high pressure and the low pressure of the air conditioning system quickly reach a complete balance state.

However, the complete balancing of the high and low pressures, while facilitating the restart of the compressor (without generating a start shock), loses the cooling or heating capacity of the air conditioning system. For example, in the cooling mode, when the compressor is just stopped, the refrigerant in the evaporator is still in a low-temperature and low-pressure state, and still has a certain evaporation cooling capacity, and if the low-temperature and low-pressure refrigerant in the evaporator is balanced with the high-temperature and high-pressure refrigerant in the condenser, the cooling capacity of the refrigerant in the evaporator is undoubtedly lost. The situation in the heating mode is similar except that the heating capacity of the refrigerant in the evaporator is lost at this time.

In order to fully utilize the residual cold or the residual heat in the indoor heat exchanger (namely an evaporator) when the compressor is stopped and further improve the annual energy efficiency of the air conditioning system, the pipeline between the indoor heat exchanger and the outdoor heat exchanger can be blocked when the compressor is stopped, and meanwhile, the operation of an indoor side fan is kept. Thus, since the pipe between the indoor heat exchanger and the outdoor heat exchanger is blocked, the refrigerant in the outdoor heat exchanger cannot be immediately mixed with the refrigerant in the indoor heat exchanger, and the refrigerant in the indoor heat exchanger still has the capacity of supplying residual cold (in a cooling mode) or supplying residual heat (in a heating mode) for a while after the compressor is stopped, so that the cooling or heating of the indoor side can be continued for a while by means of the air circulation of the indoor side fan.

In the related art air conditioning system, when the compressor is stopped, the most commonly used method for blocking the refrigerant on the high and low pressure sides is to connect a liquid solenoid valve in series between an outdoor heat exchanger and a throttling element of the refrigeration system. For example, in the cooling mode, when the compressor operates, the liquid path solenoid valve is kept open, and the cooling system continuously performs cooling operation; when the compressor stops running, the liquid path electromagnetic valve is closed, the refrigerant flow path is cut off, and the low-temperature refrigerant remained in the indoor heat exchanger can continue to supply residual cold.

However, since the liquid path solenoid valve is installed on the main liquid path of the refrigerant, the flow rate flowing through the valve port of the liquid path solenoid valve is large, the valve body of the liquid path solenoid valve must be large, and the large liquid path solenoid valve has high cost, so that the cost of the whole air conditioning system is greatly increased. In addition, because the method is to completely cut off the pipeline between the indoor heat exchanger and the outdoor heat exchanger when the compressor is stopped, the high pressure and the low pressure cannot be balanced, so when the compressor is restarted, the method can bring larger starting impact to the compressor, and therefore, the method can only be applied to the compressor which is insensitive to the starting pressure difference (such as a scroll compressor with a flexible scroll) and cannot be applied to a rotor compressor which has small starting moment and is sensitive to the starting pressure difference. In addition, some compressors employ pressure balancing devices that are inconvenient to install, have poor integrity, and are costly.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides the compressor which has the advantages of high heat exchange efficiency and annual energy efficiency, small starting impact, convenience in installation, good integrity, low cost and the like.

The invention also provides a refrigerating system with the compressor.

According to an embodiment of the first aspect of the present invention, a compressor includes: a housing having a receiving chamber, a suction port, and a discharge port; the compression mechanism is arranged in the accommodating cavity and is provided with an air suction port and an air exhaust port, the air suction port is communicated with the suction port, and the air exhaust port is communicated with the accommodating cavity; the driving mechanism is in transmission connection with the compression mechanism; a first flow direction control member, one end of which is communicated with the suction port of the compression mechanism and the other end of which is communicated with the accommodating cavity of the compression mechanism, the first flow direction control member being switchable between a state of communicating and a state of disconnecting the suction port and the accommodating cavity; the second flow direction control piece is used for controlling the unidirectional circulation of the air flow along the suction port and the compression mechanism to the discharge port; a wire connecting portion connected to the driving mechanism and the first flow direction control member, respectively.

According to the compressor provided by the embodiment of the invention, the heat exchange efficiency and the annual energy efficiency of the refrigerating system can be improved, the phenomenon of starting with pressure difference can be avoided, and the compressor is convenient to install, good in integrity and low in cost.

In addition, the compressor according to the embodiment of the present invention has the following additional technical features:

according to some embodiments of the invention, the second flow control member comprises: the inlet of the first one-way valve is connected with the accommodating cavity, and the outlet of the first one-way valve is connected with the discharge port.

According to some embodiments of the invention, the second flow control member comprises: and the inlet of the second one-way valve is connected with the suction inlet, and the outlet of the second one-way valve is connected with the suction inlet.

Further, the one end of the first flow direction control member is connected to an outlet of the second check valve.

According to some embodiments of the invention, the drive mechanism is started and stopped synchronously with the first flow control member.

According to some embodiments of the invention, the first flow control member is a normally open solenoid valve.

According to some embodiments of the invention, the two ends of the first flow control member are spaced apart when the driving mechanism drives the compression mechanism to operate, and the two ends of the first flow control member are communicated when the driving mechanism stops.

According to some embodiments of the present invention, the wire portion blocks the suction port and the accommodating chamber when the first flow direction control member is energized, and the wire portion communicates the suction port and the accommodating chamber when the first flow direction control member is de-energized.

According to some embodiments of the invention, the drive mechanism comprises: the stator assembly is arranged in the accommodating cavity and is provided with a stator winding; a rotor assembly rotatably disposed within the stator assembly; the eccentric rotating shaft is arranged in the accommodating cavity and is in transmission connection with the compression mechanism and the rotor assembly respectively.

Further, the stator winding includes main winding and secondary winding, wiring portion includes first terminal, second terminal and third terminal, first flow direction control piece has first wiring end and second wiring end, first terminal with first wiring end with the one end of main winding is connected electrically, the third terminal with the one end of secondary winding is connected electrically, the second terminal with the second wiring end, the other end of main winding and the other end of secondary winding are connected electrically, first terminal with be connected with starting capacitor between the third terminal.

In some embodiments of the invention, the compression mechanism comprises: the cylinder is provided with an inner cavity which is respectively communicated with the air suction port and the air exhaust port; and the piston is sleeved on the eccentric rotating shaft and can rotate along the inner wall of the cylinder.

According to a second aspect of the embodiment of the invention, the refrigeration system comprises: a compressor according to an embodiment of the first aspect of the present invention; the first end of the indoor heat exchanger is connected with the compressor; the first end of the outdoor heat exchanger is connected with the compressor; and the throttle valves are respectively connected with the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger.

According to the refrigeration system provided by the embodiment of the invention, the compressor is utilized, the heat exchange efficiency and the annual energy efficiency are high, the phenomenon of starting with pressure difference can be avoided, and the refrigeration system is convenient to install, good in integrity and low in cost.

According to some embodiments of the invention, the refrigeration system further comprises: the reversing valve is provided with a first interface, a second interface, a third interface and a fourth interface and can be switched between a heating state and a cooling state, the discharge port is connected with the first interface, the suction port is connected with the second interface, one end of the indoor heat exchanger is connected with the third interface, and one end of the outdoor heat exchanger is connected with the fourth interface.

According to some embodiments of the invention, the throttle valve is a leakless thermostatic expansion valve, wherein the throttle valve is conducting and throttling the refrigerant when the compressor is running; and when the compressor stops running, the throttle valve is closed to respectively block the high-pressure refrigerant or the low-pressure refrigerant in the indoor heat exchanger and the outdoor heat exchanger, so that the refrigerants in the indoor heat exchanger and the outdoor heat exchanger cannot immediately reach a pressure balance state.

Further, after the compressor stops operating, the fan corresponding to the indoor heat exchanger continues to operate for a period of time, so that residual cold or residual heat of the refrigerant blocked in the indoor heat exchanger is fully utilized.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

FIG. 1 is a schematic diagram of a refrigeration system according to an embodiment of the present invention;

FIG. 2 is a schematic diagram of a refrigeration system according to an embodiment of the present invention;

FIG. 3 is a schematic diagram of a refrigeration system according to an embodiment of the present invention;

fig. 4 is a schematic wiring diagram of a compressor according to an embodiment of the present invention.

Reference numerals:

in the case of the refrigeration system 1,

a compressor 10, a reversing valve 20, a first interface 21, a second interface 22, a third interface 23, a fourth interface 24, an indoor heat exchanger 30, an outdoor heat exchanger 40, a throttle valve 50, a gas-liquid separator 60, an outdoor side fan 70, an indoor side fan 80,

a housing 100, a receiving chamber 101, an intake port 102, an exhaust port 103,

a cylinder 210, an intake port 211, an exhaust port 212, a piston 220,

stator assembly 310, stator winding 301, main winding 311, sub-winding 312, rotor assembly 320, eccentric rotary shaft 330,

a first flow control 410, a second flow control 420, a first check valve 421, a second check valve 422,

the wiring portion 500, a first terminal 501, a second terminal 502, a third terminal 503, and a start capacitor 504.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

A compressor 10 according to an embodiment of the first aspect of the present invention is described below with reference to the accompanying drawings. For example, the compressor 10 is a rotary compressor.

As shown in fig. 1 to 4, a compressor 10 according to an embodiment of the present invention includes: the housing 100, the compression mechanism, the driving mechanism, the first flow direction controller 410, the second flow direction controller 420, and the wire connecting portion 500.

Specifically, the housing 100 has a housing chamber 101, an intake port 102, and an exhaust port 103. The compression mechanism is provided in the housing chamber 101, and has a suction port 211 and an exhaust port 212, the suction port 211 communicating with the suction port 102, and the exhaust port 212 communicating with the housing chamber 101. The driving mechanism is arranged in the accommodating cavity 101 and is in transmission connection with the compression mechanism so as to drive the compression mechanism to operate.

One end of the first flow direction control member 410 is communicated with the suction port 211 of the compression mechanism, and the other end of the first flow direction control member 410 is communicated with the accommodation chamber 101, and the first flow direction control member 410 is switchable between a state of communicating and disconnecting the suction port 211 and the accommodation chamber 101. The second flow control member 420 is used to control the flow of air (i.e., refrigerant) in one direction along the suction port 102, the compression mechanism, and to the discharge port 103. The wire connection portion 500 is connected to the driving mechanism and the first flow direction control member 410, respectively.

Specifically, when the compressor 10 is operated, the suction port 102 communicates with the suction port 211 and the discharge port 103 communicates with the receiving chamber 101. At this time, the suction port 211 is disconnected from the receiving chamber 101, and the flow path of the refrigerant in the compressor 10 is: the refrigerant enters from the suction port 102, is sucked into the compression mechanism through the suction port 211, is compressed in the compression mechanism, increases in pressure, and is discharged out of the compression mechanism through the discharge port 212; the refrigerant discharged from the compression mechanism enters the accommodation chamber 101, and is finally discharged from the compressor 10 through the discharge port 103.

When the compressor 10 stops operating, the throttle valve of the refrigeration system can separate the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant; meanwhile, the suction port 211 communicates with the upper space of the receiving chamber 101, so that the pressure of the refrigerant in the receiving chamber 101 is a low pressure equal to the pressure at the suction port 211. At the moment, residual cold or residual heat of the refrigerant remained in the outdoor heat exchanger and the indoor heat exchanger can be utilized to improve the energy utilization efficiency of the heat exchange system and improve the seasonal energy efficiency ratio of the heat exchange system; meanwhile, since the suction port 211 is communicated with the upper space of the accommodating chamber 101, the discharge pressure and the suction pressure of the compressor 10 can be sufficiently balanced, and the phenomenon of starting with pressure difference when the compressor 10 is restarted can be avoided.

Therefore, according to the compressor 10 provided by the embodiment of the invention, the heat exchange efficiency and the annual energy efficiency can be improved, and meanwhile, the phenomenon of starting with differential pressure can be avoided; in addition, the first flow control member 410 is arranged in the accommodating cavity 101, so that a connecting line between the first flow control member 410 and the wiring portion 500 can be also positioned in the accommodating cavity 101, and compared with a balance structure arranged outside the compressor, the balance structure not only can facilitate the connection between the first flow control member 410 and the wiring portion 500, but also has a compact structure and good integrity, saves a plurality of connecting structures, and reduces the cost.

To this end, as shown in fig. 1 and 3, the second flow direction control member 420 includes: a first check valve 421, an inlet of the first check valve 421 is connected to the receiving chamber 101 and an outlet of the first check valve 421 is connected to the discharge port 103. In this way, the first check valve 421 controls the one-way conduction of the air flow along the direction from the accommodating chamber 101 to the discharge port 103, so as to reliably stop the air flow when the compressor 10 stops operating, and has simple structure and low cost.

Specifically, when the compression mechanism operates, the first flow direction control element 410 is closed, the suction port 211 is disconnected from the accommodating cavity 101, the pressure of the refrigerant discharged by the compression mechanism is higher, the pressure at the inlet of the first check valve 421 is higher than the pressure at the outlet, and the first check valve 421 is connected, so that the refrigerant can enter the compression mechanism through the suction port 211, and is discharged out of the compressor 10 through the discharge port 212 and the discharge port 103 after being compressed by the compression mechanism, thereby realizing the normal operation of the compressor 10.

When the compressor 10 stops operating, the first flow direction control member 410 is conducted, the suction port 211 is communicated with the accommodating chamber 101, the pressure of the refrigerant in the accommodating chamber 101 is reduced to be equal to the pressure at the suction port 211, at this time, the pressure at the inlet of the first check valve 421 is not higher than the pressure at the outlet, the first check valve 421 is cut off, and the flow path between the indoor heat exchanger and the outdoor heat exchanger is blocked, so that the residual cold or residual heat of the refrigerant in the indoor heat exchanger can be fully utilized.

According to some embodiments of the present invention, as shown in fig. 2 and 3, the second flow control member 420 includes: a second check valve 422, an inlet of the second check valve 422 being connected to the suction port 102 and an outlet of the second check valve 422 being connected to the suction port 211 and the one end of the first flow direction control member 410. In this way, the second check valve 422 controls the airflow to be conducted in one direction from the suction port 102 to the suction port 211, so as to reliably stop the airflow when the compressor 10 stops operating, and has a simple structure and low cost.

Specifically, when the compression mechanism is operated, the refrigerant is sucked into the compression mechanism from the suction port 102, the second check valve 422, the suction port 211, compressed in the compression mechanism, and then increased in pressure, and then discharged from the discharge port 212 to the upper space (i.e., the accommodating chamber 101) in the casing 100, and further discharged out of the compressor 10 through the discharge port 103; when the compressor 10 stops operating, since the refrigerant in the casing 100 is still in a high pressure state at the time of shutdown, the pressure at the outlet of the second check valve 422 is greater than the pressure at the inlet by the conduction of the first flow direction control member 410, and the second check valve 422 is blocked to block the flow path between the indoor heat exchanger and the outdoor heat exchanger, so that the residual cold or the residual heat of the refrigerant remaining in the indoor heat exchanger can be fully utilized.

Of course, as shown in fig. 3, the accommodating chamber 101 may be provided with a first check valve 421 and a second check valve 422 at the same time, the first check valve 421 controls the refrigerant to flow from the accommodating chamber 101 to the discharge port 103 in one direction, and the second check valve 422 controls the refrigerant to flow from the suction port 102 to the suction port 211 in one direction, so that the flow path between the indoor heat exchanger and the outdoor heat exchanger can be blocked more reliably when the compressor 10 stops operating.

According to some embodiments of the present invention, as shown in fig. 1-4, the driving mechanism is started and stopped synchronously with the first flow control 410, that is, when the compressor 10 is operated, the driving mechanism is powered on and the first flow control 410 is powered on; when compressor 10 is stopped, the drive mechanism is de-energized and stopped and first flow control 410 is de-energized, thereby facilitating both wiring and control.

According to some embodiments of the present invention, as shown in fig. 1-4, the first flow control member 410 is a normally open solenoid valve, that is, when the first flow control member 410 is de-energized, both ends of the first flow control member 410 are open, and when the first flow control member 410 is energized, both ends of the first flow control member 410 are open. For example, the first flow direction controller 410 has a coil electrically connected to the wire connection portion 500, the first flow direction controller 410 is switched to a cut-off state when the wire connection portion 500 supplies power to the coil, and the first flow direction controller 410 is switched to a connected state when the wire connection portion 500 disconnects power to the coil.

According to some embodiments of the present invention, as shown in fig. 1-4, the two ends of the first flow control member 410 are spaced apart when the compression mechanism is operated by the driving mechanism, and the two ends of the first flow control member 410 are connected when the compression mechanism is stopped. In this way, when the compressor 10 is operated, the compression mechanism is operated and the suction port 211 is disconnected from the receiving chamber 101; when the compressor 10 stops operating, the compression mechanism stops operating and the suction port 211 communicates with the receiving chamber 101, thereby achieving a balance between high and low pressures.

According to some embodiments of the present invention, as shown in fig. 1 to 4, the wire connection portion 500 isolates the suction port 211 from the accommodating chamber 101 when the first flow direction controller 410 is energized, and the wire connection portion 500 communicates the suction port 211 with the accommodating chamber 101 when the first flow direction controller 410 is de-energized, so that the first flow direction controller 410 and the driving mechanism can be synchronously started and stopped.

According to some embodiments of the invention, as shown in fig. 1-3, the drive mechanism comprises: a stator assembly 310, a rotor assembly 320, and an eccentric rotating shaft 330. The stator assembly 310 is disposed in the accommodating chamber 101, and the stator assembly 310 has stator windings 301. The rotor assembly 320 is rotatably disposed within the stator assembly 310. The eccentric rotating shaft 330 is disposed in the accommodating cavity 101, and the eccentric rotating shaft 330 is in transmission connection with the compression mechanism and the rotor assembly 320, respectively. Thus, when the wiring portion 500 is energized, the compression mechanism operates; when the wiring portion 500 is powered off, the compression mechanism stops operating.

Further, the stator winding 301 includes a main winding 311 and a sub-winding 312, the wiring portion 500 includes a first terminal 501, a second terminal 502, and a third terminal 503, the coil has a first terminal and a second terminal, the first terminal 501 is electrically connected to the first terminal and one end of the main winding 311, the third terminal 503 is electrically connected to one end of the sub-winding 312, the second terminal 502 is electrically connected to the second terminal, the other end of the main winding 311, and the other end of the sub-winding 312, and a start capacitor 504 is connected between the first terminal 501 and the third terminal 503.

Thus, when the wiring part 500 applies an alternating current between the first terminal 501 and the second terminal 502, the compressor 10 is operated and the first flow direction control member 410 cuts off the suction port 211 and the receiving chamber 101; when the wiring portion 500 disconnects the alternating current between the first terminal 501 and the second terminal 502, the compressor 10 stops operating and the first flow direction control member 410 communicates the suction port 211 and the receiving chamber 101.

In some embodiments of the present invention, as shown in fig. 1-3, the compression mechanism includes a cylinder 210 and a piston 220. The piston 220 is sleeved on the eccentric rotating shaft 330, and the piston 220 can rotate along the inner wall of the cylinder 210. In this way, compression of the refrigerant is achieved.

As shown in fig. 1 to 4, a refrigeration system 1 according to an embodiment of the second aspect of the present invention includes: the compressor 10, the reversing valve 20, the indoor heat exchanger 30, the outdoor heat exchanger 40, and the throttle valve 50 according to the embodiment of the first aspect of the present invention. For example, the refrigeration system 1 may be an air conditioning system.

Specifically, the selector valve 20 has a first port 21, a second port 22, a third port 23, and a fourth port 24, and the discharge port 103 is connected to the first port 21 and the suction port 102 is connected to the second port 22; one end of the indoor heat exchanger 30 is connected to the third port 23; one end of the outdoor heat exchanger 40 is connected to the fourth port 24.

The direction valve 20 is switchable between a heating state and a cooling state, the first port 21 is communicated with the third port 23 and the second port 22 is communicated with the fourth port 24 when the direction valve 20 is in the heating state, and the first port 21 is communicated with the fourth port 24 and the second port 22 is communicated with the third port 23 when the direction valve 20 is in the cooling state.

The throttle valves 50 are connected to the other end of the indoor heat exchanger 30 and the other end of the outdoor heat exchanger 40, respectively. Throttle 50 may be a leakless thermostatic expansion valve. The leakless thermostatic expansion valve is conducted when the compressor 10 is in operation and the high-low pressure difference is large, the refrigerant at the high-pressure side can pass through a valve hole in the leakless thermostatic expansion valve, and at the moment, the leakless thermostatic expansion valve plays a role in throttling the refrigerant.

The leakless thermostatic expansion valve is stopped when the compressor 10 stops operating and the difference between high and low pressures is small, and the refrigerant at the high pressure side cannot pass through a valve hole inside the leakless thermostatic expansion valve, at this time, the leakless thermostatic expansion valve plays a role in blocking, namely, the high-pressure refrigerant, the high-temperature refrigerant, the low-pressure refrigerant and the low-temperature refrigerant are respectively blocked in the outdoor heat exchanger 40 and the indoor heat exchanger 30, and the refrigerants in the indoor heat exchanger and the outdoor heat exchanger cannot reach a pressure and temperature balance state immediately, so that the heat exchange efficiency and the annual energy efficiency can be improved, and the high and low pressures can be balanced by using the pressure balance assembly when the.

According to the refrigeration system 1 provided by the embodiment of the invention, the compressor 10 is utilized, so that the heat exchange efficiency and the annual energy efficiency are high, the phenomenon of starting with pressure difference can be avoided, and the refrigeration system is convenient to install, good in integrity and low in cost.

A refrigeration system 1 according to an embodiment of the present invention is described in detail below with reference to the drawings.

In the embodiment shown in fig. 1, the refrigeration system 1 includes a compressor 10, a direction change valve 20, an indoor heat exchanger 30, an outdoor heat exchanger 40, a throttle valve 50, a gas-liquid separator 60, an outdoor side fan 70, and an indoor side fan 80.

Here, the compressor 10 is a high-back-pressure compressor, that is, when the compressor 10 is in an operating state, the space in the housing 100 (i.e., the accommodating chamber 101) outside the cylinder 210 is filled with high-pressure gas, that is, the background pressure of the compressor 10 is in a high-pressure state. The inlet of the gas-liquid separator 60 is connected to the second connection port 22, and the outlet of the gas-liquid separator 60 is connected to the suction port 102.

In this embodiment, the outlet of the first check valve 421 communicates with the discharge port 103 and the inlet communicates with the accommodation chamber 101. One end of the first flow direction control member 410 communicates with the suction port 211 and the suction port 102, respectively, and the other end of the first flow direction control member 410 communicates with the accommodation chamber 101.

Wherein the first flow direction control member 410 is a normally open solenoid valve, the compressor 10 is operated and the first flow direction control member 410 is in a cut-off state when alternating current is applied between the first and second terminals (the first and second terminals 501 and 502) of the coil; when ac power is disconnected between the first terminal and the second terminal, the compressor 10 stops operating and the first flow control member 410 is in a connected state.

The working characteristics of the compressor 10 in this embodiment are: when the pressure inside the casing 100 is higher than the pressure at the discharge port 103, the refrigerant can flow out of the discharge port 103 from inside the casing 100 but cannot flow back into the casing 100 from the discharge port 103; when the pressure in the casing 100 is lower than the pressure at the discharge port 103, the refrigerant cannot flow from the inside of the casing 100 to the outside of the compressor 10, nor from the outside of the compressor 10 to the inside of the casing 100. That is, the refrigerant in the present embodiment can flow out of the discharge port 103 only in one direction from the accommodation chamber 101.

As shown in the embodiment of fig. 1, residual cooling (or residual heat) utilization when the compressor 10 is normally operated and the compressor 10 is stopped may be achieved, so that seasonal energy efficiency of the air conditioning system may be improved.

When the compressor 10 is normally operating, the first flow control member 410 is in a cut-off state. At this time, the flow path of the refrigerant in the compressor 10 is: the refrigerant enters the compressor 10 from the suction port 102, is sucked into the cylinder 210 through the suction port 211, is compressed in the cylinder 210, increases in pressure, and is discharged out of the cylinder 210 from the discharge port 212; then, the refrigerant discharged from the cylinder 210 passes through the gap between the stator assembly 310 and the casing 100 to reach the upper space in the casing 100, and since the discharge pressure is high at this time and the first check valve 421 is turned on, the refrigerant can be discharged out of the compressor 10 through the first check valve 421 and the discharge port 103.

Specifically, when the refrigeration system 1 is in the refrigeration cycle mode (the reversing valve 20 is switched to the cooling state), the circulation path of the refrigerant discharged from the compressor 10 outside the compressor 10 is: the discharge port 103 → the first port 21 → the fourth port 24 → the outdoor heat exchanger 40 → the throttle valve 50 → the indoor heat exchanger 30 → the third port 23 → the second port 22 → the gas-liquid separator 60 → the suction port 102, thus forming a complete refrigeration cycle. In the refrigeration cycle mode, the refrigerant in the outdoor heat exchanger 40 is in a high-pressure condensation state, the refrigerant in the indoor heat exchanger 30 is in a low-pressure evaporation state, and both sides of the throttle valve 50 are in a large pressure difference state, so that the leakless thermostatic expansion valve is in a conductive and normally throttled state.

When the refrigeration system 1 is in the heating cycle mode (the reversing valve 20 is switched to the heating state), the circulation path of the refrigerant outside the compressor 10 is: the discharge port 103 → the first port 21 → the third port 23 → the indoor heat exchanger 30 → the throttle valve 50 → the outdoor heat exchanger 40 → the fourth port 24 → the second port 22 → the gas-liquid separator 60 → the suction port 102. In the heating cycle mode, the refrigerant in the indoor heat exchanger 30 is in a high-pressure condensation state, the refrigerant in the outdoor heat exchanger 40 is in a low-pressure evaporation state, and both sides of the throttle valve 50 are in a large pressure difference state, so that the leakless thermostatic expansion valve is in a conducting and normally throttling state.

As shown in fig. 1, when the compressor 10 is just stopped, the coil of the first flow control member 410 is de-energized, the first flow control member 410 is turned on, the pressure in the casing 100 is a low pressure equal to the pressure at the suction port 102 and the second port 22, and the first check valve 421 is turned off; meanwhile, since the valve port of the leakless thermostatic expansion valve is closed when the compressor 10 is stopped, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are blocked at both sides of the leakless thermostatic expansion valve and cannot be mixed with each other.

Thus, the residual cold or residual heat of the refrigerant remaining in the outdoor heat exchanger 40 and the indoor heat exchanger 30 after the compressor 10 is stopped can be fully utilized to improve the energy utilization efficiency and the seasonal energy efficiency ratio of the refrigeration system 1, and the discharge pressure and the suction pressure of the compressor 10 can be fully balanced to avoid the compressor 10 from being started with a pressure difference.

The following description will be made for the case of cooling and heating, respectively:

when the refrigeration system 1 is in the refrigeration cycle mode and the compressor 10 is just stopped, the compressor 10 does not continuously apply work to the refrigerant, so that the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 is reduced, and when the pressure difference is reduced to the stop pressure of the leakless thermostatic expansion valve, the leakless thermostatic expansion valve is stopped.

Due to the conduction of the first flow direction control member 410, the high-pressure refrigerant in the casing 100 passes through the first flow direction control member 410, the gas-liquid separator 60, the second port 22 and the third port 23, and then releases the pressure to the indoor heat exchanger 30 on the low-pressure side, so that finally, the pressure in the casing 100, the pressure at the suction port 211 and the pressure of the refrigerant in the indoor heat exchanger 30 tend to be equal, that is, are all in a low-pressure state.

The low pressure state in the casing 100 effectively reduces the exhaust resistance of the cylinder 210, avoids the phenomena of over-high starting current, difficult starting, impact, vibration and the like of the compressor 10 starting with pressure difference when the compressor 10 is restarted, and is beneficial to prolonging the service life of the compressor 10.

Meanwhile, since the interior of the casing 100 is in a low-pressure state and the refrigerant in the outdoor heat exchanger 40 is still in a high-pressure state when the compressor is stopped, the first check valve 421 will be closed, and the high-pressure refrigerant in the outdoor heat exchanger 40 cannot flow back into the casing 100 through the first check valve 421, so that the high-temperature refrigerant with still higher temperature is blocked in the outdoor heat exchanger 40, and the refrigerant with still lower temperature is blocked in the indoor heat exchanger 30, and the high-temperature refrigerant and the low-temperature refrigerant cannot be mixed with each other, thereby respectively retaining the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant when the compressor 10 is stopped.

At this time, if the indoor side fan 80 is still running, the cooling capacity in the indoor heat exchanger 30 can be taken away to continue cooling the indoor air, so that the residual cooling in the indoor heat exchanger 30 is fully utilized, the energy efficiency ratio of the refrigeration season of the refrigeration system 1 can be effectively improved, and the refrigeration system 1 is more energy-saving.

When the refrigeration system 1 is in the heating circulation mode and the compressor 10 is just stopped, the compressor 10 does not continuously compress the refrigerant, so that the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 is reduced, and when the pressure difference is reduced to the stop pressure of the leakless thermostatic expansion valve, the leakless thermostatic expansion valve is stopped. Since the first flow direction control member 410 is turned on, the high-pressure refrigerant in the casing 100 passes through the first flow direction control member 410, the gas-liquid separator 60, the second port 22, and the fourth port 24, and then releases the pressure to the outdoor heat exchanger 40 on the low-pressure side, and finally, the pressure in the casing 100, the pressure at the suction port 211, and the pressure of the refrigerant in the outdoor heat exchanger 40 tend to be equal, that is, are all in a low-pressure state.

Meanwhile, since the interior of the casing 100 is in a low-pressure state and the refrigerant in the indoor heat exchanger 30 is still in a high-pressure state when the compressor is stopped, the high-pressure refrigerant in the indoor heat exchanger 30 cannot flow back into the casing 100 through the first check valve 421, so that the refrigerant with still higher temperature is blocked in the indoor heat exchanger 30, and the refrigerant with still lower temperature is blocked in the outdoor heat exchanger 40, the high-temperature refrigerant and the low-temperature refrigerant cannot be mixed with each other, and thus the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant are respectively maintained when the compressor 10 is stopped.

At this time, if the indoor side fan 80 is still running, the heat in the indoor heat exchanger 30 can be taken away to continue to heat the indoor air, so that the waste heat in the indoor heat exchanger 30 is fully utilized, the energy efficiency ratio of the refrigerating system 1 in the heating season can be effectively improved, and the refrigerating system 1 is more energy-saving.

The difference between the embodiment shown in fig. 2 and the embodiment shown in fig. 1 is that the inlet of the second check valve 422 shown in fig. 2 communicates with the suction port 102, and the one end of the first flow direction control member 410 communicates with the outlet of the second check valve 422 and the suction port 211, respectively.

In the embodiment illustrated in FIG. 2, the first flow control member 410 is in a deactivated state when the compressor 10 is operating. At this time, the flow path of the refrigerant in the compressor 10 is: the refrigerant is sucked into the cylinder 210 through the suction port 102, the second check valve 422 and the suction port 211, compressed in the cylinder 210, and then increased in pressure, and discharged out of the cylinder 210 through the discharge port 212; the refrigerant discharged out of the cylinder 210 passes through the gap between the stator assembly 310 and the casing 100 to reach the upper space in the casing 100, and is discharged out of the compressor 10 through the discharge port 103.

When the refrigeration system 1 is in the refrigeration cycle mode, the circulation path of the refrigerant discharged from the compressor 10 outside the compressor 10 is: the discharge port 103 → the first port 21 → the fourth port 24 → the outdoor heat exchanger 40 → the throttle valve 50 → the indoor heat exchanger 30 → the third port 23 → the second port 22 → the gas-liquid separator 60 → the suction port 102, thus forming a complete refrigeration cycle. In the refrigeration cycle mode, the refrigerant in the outdoor heat exchanger 40 is in a high-pressure condensation state, the refrigerant in the indoor heat exchanger 30 is in a low-pressure evaporation state, and both sides of the throttle valve 50 are in a large pressure difference state, so that the leakless thermostatic expansion valve is in a conductive and normally throttled state.

When the refrigeration system 1 is in the heating cycle mode, the circulation path of the refrigerant outside the compressor 10 is: the discharge port 103 → the first port 21 → the third port 23 → the indoor heat exchanger 30 → the throttle valve 50 → the outdoor heat exchanger 40 → the fourth port 24 → the second port 22 → the gas-liquid separator 60 → the suction port 102. In the heating cycle mode, the refrigerant in the indoor heat exchanger 30 is in a high-pressure condensation state, the refrigerant in the outdoor heat exchanger 40 is in a low-pressure evaporation state, and both sides of the throttle valve 50 are in a large pressure difference state, so that the leakless thermostatic expansion valve is in a conducting and normally throttling state.

As shown in fig. 2, when the compressor 10 just stops operating, the coil of the first flow control member 410 is de-energized and the first flow control member 410 is turned on. Because the interior of the housing 100 is at a high pressure when the engine is just stopped, the first flow direction control element 410 is turned on, so that the outlet of the second check valve 422 is at a high pressure state, and the second check valve 422 is turned off; meanwhile, since the valve port of the leakless thermostatic expansion valve is closed when the compressor 10 is stopped, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are blocked at both sides of the leakless thermostatic expansion valve and cannot be mixed with each other.

Because the first flow direction control element 410 is conducted, the pressure at the air suction port 211 is balanced with the pressure in the shell 100, that is, the pressure at the air suction port 211 of the air cylinder 210 is equal to the pressure at the air exhaust port 212, so that the starting torque of the compressor 10 is small, the phenomena of over-high starting current, difficult starting, impact, vibration and other pressure difference starting phenomena when the compressor 10 is started again are avoided, and the service life of the compressor 10 is prolonged.

Meanwhile, since the interior of the casing 100 is in a high-pressure state during shutdown, the interior of the indoor heat exchanger 30 is still in a low-pressure state, and the second check valve 422 is in a cut-off state, the low-pressure refrigerant in the indoor heat exchanger 30 cannot flow back into the casing 100 through the second check valve 422, so that the refrigerant with still low temperature is blocked in the indoor heat exchanger 30, the high-temperature refrigerant with still high temperature is blocked in the outdoor heat exchanger 40, and the high-temperature refrigerant and the low-temperature refrigerant cannot be mixed with each other, thereby respectively retaining the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant when the compressor 10 is shutdown.

When the refrigeration system 1 is in the heating circulation mode and the compressor 10 is just stopped, the compressor 10 does not continuously compress the refrigerant, so that the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 is reduced, and when the pressure difference is reduced to the stop pressure of the leakless thermostatic expansion valve, the leakless thermostatic expansion valve is stopped. Because the first flow direction control element 410 is conducted, the pressure at the air suction port 211 is balanced with the pressure in the shell 100, that is, the pressure at the air suction port 211 of the air cylinder 210 is equal to the pressure at the air exhaust port 212, so that the starting torque of the compressor 10 can be effectively reduced, and the phenomena of overlarge starting current, difficult starting, impact, vibration and the like of differential pressure starting of the compressor 10 when the compressor 10 is restarted are avoided.

Meanwhile, since the interior of the casing 100 is in a high-pressure state and the interior of the outdoor heat exchanger 40 is still in a low-pressure state when the compressor is stopped, the low-pressure refrigerant in the outdoor heat exchanger 40 cannot flow back into the casing 100 through the second check valve 422, so that the refrigerant with still lower temperature is blocked in the outdoor heat exchanger 40, and the refrigerant with still higher temperature is blocked in the indoor heat exchanger 30, and the high-temperature refrigerant and the low-temperature refrigerant cannot be mixed with each other, thereby respectively retaining the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant when the compressor 10 is stopped.

At this time, if the indoor side fan 80 is still running, the heat in the indoor heat exchanger 30 can be taken away, and the indoor air is continuously heated, so that the waste heat in the indoor heat exchanger 30 is fully utilized, the energy efficiency ratio of the refrigerating system 1 in the heating season can be effectively improved, and the refrigerating system 1 is more energy-saving.

The embodiment shown in fig. 3 is the addition of a first one-way valve 421 to the embodiment shown in fig. 2, wherein the outlet of the first one-way valve 421 is communicated with the discharge port 103 and the inlet is communicated with the accommodating chamber 101. The normal operation process and the shutdown protection process of the compressor 10 of the present embodiment can refer to the embodiments of fig. 1-2, and are not described herein again.

In short, according to the refrigeration system 1 of the embodiment of the present invention, the switch combination state of the check valve and the solenoid valve is utilized to maintain the high-low pressure difference in the indoor heat exchanger 30 and the outdoor heat exchanger 40 when the compressor 10 is stopped, so as to fully utilize the residual cold or the residual heat in the indoor heat exchanger 30 after the compressor 10 is stopped; meanwhile, the pressure inside the compressor 10 is rapidly balanced to ensure smooth start when the compressor 10 is started again, thereby ensuring the safety of the start of the compressor 10.

In addition, because the check valve and the solenoid valve are both arranged in the accommodating cavity 101, the installation process can be greatly simplified, the pipeline connection is convenient, the structure is very compact, and the cost of the check valve and the cost of the solenoid valve are both lower, so that the compressor 10 according to the embodiment of the invention can improve the energy efficiency of the refrigerating system 1, and simultaneously achieve the purposes of facilitating the assembly of the refrigerating system 1, improving the integrity of the refrigerating system 1 and reducing the cost of the refrigerating system 1.

Other constructions and operations of the refrigeration system 1 according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.

In the description of the present invention, it is to be understood that the terms "central", "upper", "lower", "top", "bottom", "inner", "outer", "circumferential", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are used only for convenience in describing the present invention and for simplification of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second", "third", "fourth" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first", "second", "third", "fourth" may explicitly or implicitly include one or more of the features. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; either directly or indirectly through intervening media, or through the communication between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "a specific embodiment," "an example" or "some examples" or the like are intended to mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, comprising:

a housing having a receiving chamber, a suction port, and a discharge port;

the compression mechanism is arranged in the accommodating cavity and is provided with an air suction port and an air exhaust port, the air suction port is communicated with the suction port, and the air exhaust port is communicated with the accommodating cavity;

the driving mechanism is in transmission connection with the compression mechanism;

a first flow direction control member, one end of which is communicated with the suction port of the compression mechanism and the other end of which is communicated with the accommodating cavity of the compression mechanism, the first flow direction control member being switchable between a state of communicating and a state of disconnecting the suction port and the accommodating cavity;

the second flow direction control piece is used for controlling the unidirectional circulation of the air flow along the suction port and the compression mechanism to the discharge port;

a wire connecting portion connected to the driving mechanism and the first flow direction control member, respectively.

2. The compressor of claim 1, wherein the second flow control member comprises:

the inlet of the first one-way valve is connected with the accommodating cavity, and the outlet of the first one-way valve is connected with the discharge port.

3. The compressor of claim 1 or 2, wherein the second flow control member comprises:

and the inlet of the second one-way valve is connected with the suction inlet, and the outlet of the second one-way valve is connected with the suction inlet.

4. The compressor of claim 3, wherein the one end of the first flow control member is connected to an outlet of the second one-way valve.

5. The compressor of claim 1, wherein the drive mechanism is started and stopped in synchronization with the first flow control.

6. The compressor of claim 1, wherein the first flow control member is a normally open solenoid valve.

7. The compressor of claim 1, wherein the ends of the first flow control member are spaced apart when the drive mechanism drives the compression mechanism, and wherein the ends of the first flow control member are open when the drive mechanism is deactivated.

8. The compressor of claim 1, wherein the wire portion blocks the suction port and the receiving chamber when the first flow direction control member is energized, and the wire portion communicates the suction port and the receiving chamber when the first flow direction control member is de-energized.

9. The compressor of any one of claims 1-2, 5-8, wherein the drive mechanism comprises:

the stator assembly is arranged in the accommodating cavity and is provided with a stator winding;

a rotor assembly rotatably disposed within the stator assembly;

the eccentric rotating shaft is arranged in the accommodating cavity and is in transmission connection with the compression mechanism and the rotor assembly respectively.

10. The compressor of claim 9, wherein the stator winding includes a main winding and a secondary winding, the wiring portion includes a first terminal, a second terminal, and a third terminal, the first flow direction control member has a first terminal and a second terminal, the first terminal is electrically connected to the first terminal and one end of the main winding, the third terminal is electrically connected to one end of the secondary winding, the second terminal is electrically connected to the second terminal, the other end of the main winding, and the other end of the secondary winding, and a start capacitor is connected between the first terminal and the third terminal.

11. The compressor of claim 9, wherein the compression mechanism comprises:

a cylinder having an inner cavity in communication with the suction port and the exhaust port;

and the piston is sleeved on the eccentric rotating shaft and can rotate along the inner wall of the cylinder.

12. A refrigeration system, comprising:

a compressor according to any one of claims 1-11;

the first end of the indoor heat exchanger is connected with the compressor;

the first end of the outdoor heat exchanger is connected with the compressor;

and the throttle valves are respectively connected with the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger.

13. The refrigeration system of claim 12, further comprising:

the reversing valve is provided with a first interface, a second interface, a third interface and a fourth interface, can be switched between a heating state and a cooling state, the discharge port is connected with the first interface, the suction port is connected with the second interface,

one end of the indoor heat exchanger is connected with the third interface, and one end of the outdoor heat exchanger is connected with the fourth interface.

14. The refrigerant system as set forth in claim 12, wherein said throttling valve is a leakless thermostatic expansion valve,

wherein the throttle valve is turned on and throttles refrigerant when the compressor is operating;

and when the compressor stops running, the throttle valve is closed to respectively block the high-pressure refrigerant or the low-pressure refrigerant in the indoor heat exchanger and the outdoor heat exchanger, so that the refrigerants in the indoor heat exchanger and the outdoor heat exchanger cannot immediately reach a pressure balance state.

15. The refrigeration system of claim 14, wherein the fan corresponding to the indoor heat exchanger continues to operate for a period of time after the compressor stops operating to fully utilize residual cooling or heat of the refrigerant blocked in the indoor heat exchanger.