CN216347151U

CN216347151U - Dual-mode refrigeration system

Info

Publication number: CN216347151U
Application number: CN202122884291.3U
Authority: CN
Inventors: 林海佳; 黄玉优; 赵材波; 康建; 李蓉
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-11-23
Filing date: 2021-11-23
Publication date: 2022-04-19
Anticipated expiration: 2031-11-23

Abstract

The utility model provides a dual-mode refrigeration system which comprises a compressor, a condenser, an evaporator, a differential pressure driving type four-way valve and a one-way valve, wherein the four-way valve comprises a valve body, a sliding body, a pipe D, a pipe C, a pipe S, a pipe E, a first communicating pipe and a second communicating pipe, the sliding body is arranged in the valve body and can slide in the valve body, the pipe D, the pipe C, the pipe S and the pipe E are respectively communicated with the inside of the valve body, the valve body comprises a piston chamber A and a piston chamber B, one end of the first communicating pipe is communicated with the pipe D, the other end of the first communicating pipe is communicated with the piston chamber A so as to introduce pressure into the piston chamber A from the pipe D, one end of the second communicating pipe is communicated with the pipe S, and the other end of the second communicating pipe is communicated with the piston chamber B so as to introduce pressure into the piston chamber B from the pipe. According to the utility model, an electromagnetic coil is not needed to drive the four-way valve, so that the waste of electric energy is avoided, the electric energy is saved, and the service life and the reliability of the control valve and the refrigeration system are improved; and simplifies the design and control complexity of the controller.

Description

Dual-mode refrigeration system

Technical Field

The utility model relates to the technical field of refrigeration, in particular to a dual-mode refrigeration system.

Background

With the great application of 4G and the gradual popularization of 5G, the heat productivity of various data processing devices is increasing, and the requirements of data centers on the cooling capacity and the energy conservation of air conditioning equipment are also increasing.

The data center is cooled by adopting an outdoor natural cold source in a transition season and a cold winter, the operating cost of air conditioning equipment can be greatly reduced, and the energy efficiency ratio is very high during normal operation by adopting a fluorine pump air conditioner. When the outdoor temperature is low, the fluorine pump mode is started, the operation of the compressor is stopped, and the fluorine pump is used for driving the refrigerant to realize the heat pipe refrigeration operation, so that the operation cost of the equipment is greatly reduced.

Split air conditioning units typically employ mechanically driven split heat pipes, such as fluorine pumps, e.g., liquid or air pumps, to drive the heat pipes. The fluorine pump heat pipe system and the heat pump system have two combination modes: 1) when the fluorine pump heat pipe and the heat pump share the system, a mode of parallel design of a throttling element and the fluorine pump is generally adopted. When the heat pump operates, the electromagnetic valve is closed, and the refrigerant performs pressure reduction operation through the throttling element; when the fluorine pump heat pipe operates, the electromagnetic valve is opened, the refrigerant is mainly driven by the fluorine pump to operate, the compressor is bypassed after passing through the one-way valve, and the compressor which stops operating has a good stopping effect, so that the refrigerant cannot pass through the compressor at the moment, and the gas refrigerant is arranged at the two ends of the compressor at the moment, so that the liquid refrigerant cannot enter the compressor, and the safety of the next start of the compressor is ensured. The combination of a fluorine pump heat pipe and a heat pump shared system can reduce a plurality of parts, but the debugging and the optimization of the system are very complicated problems. 2) The fluorine pump heat pipe and the heat pump are arranged in an independent system. The optimization and control of two independent systems are simple, and the two independent systems can be matched with each other to realize more flexible load matching, but the whole equipment has more parts, larger structure and higher cost.

There are many product technologies and patent technologies related to the air conditioning equipment composed of the above 2 nd independent heat pipe system and heat pump system, and the heat pipes are mainly used to transfer the cold energy of the outdoor natural cold source (cold air) in winter or transition season into the data center for refrigeration.

However, in the above-mentioned 1 st fluorine pump heat pipe compression dual-mode refrigeration system, the electromagnetic valve and the check valve are usually necessary components, and long-term power-on operation of the electromagnetic valve causes waste of electric energy, and the service life and reliability are reduced. The parallel structure of the throttling element, the fluorine pump and the electromagnetic valve is integrated and optimized, and a novel four-way valve is developed for the refrigerating system, so that the design is simplified.

The utility model provides a double-mode refrigeration system, which is researched and designed because the technical problems that the service life and the reliability are reduced and the like due to the electric energy waste caused by the long-term power-on operation of an electromagnetic valve exist in the double-mode refrigeration system of fluorine pump heat pipe compression in the prior art.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem to be solved by the utility model is to overcome the defects of electric energy waste and reduced service life and reliability caused by long-term power-on operation of the electromagnetic valve in the fluorine pump heat pipe compression dual-mode refrigeration system in the prior art, thereby providing a dual-mode refrigeration system.

In order to solve the above problems, the present invention provides a dual mode refrigeration system, comprising:

the compressor, the condenser, the evaporator, the differential pressure driving four-way valve and the one-way valve, wherein the differential pressure driving four-way valve comprises a valve body, a sliding body, a D pipe, a C pipe, an S pipe, an E pipe, a first communicating pipe and a second communicating pipe, the sliding body is arranged in the valve body and can slide in the valve body, the D pipe, the C pipe, the S pipe and the E pipe are respectively communicated with the interior of the valve body, the valve body comprises a piston chamber A positioned on one side of the reciprocating motion of the sliding body and a piston chamber B positioned on the other side of the reciprocating motion, one end of the first communication pipe is communicated with the D pipe, the other end of the first communication pipe is communicated with the piston chamber A so as to introduce pressure from the D pipe into the piston chamber A, one end of the second communication pipe is communicated with the S pipe, and the other end of the second communication pipe is communicated with the piston chamber B so as to introduce pressure from the S pipe into the piston chamber B;

the D pipe with the condenser intercommunication, C pipe, S pipe and E pipe equally divide respectively with the one end intercommunication of evaporimeter, the check valve is parallelly connected to be set up the both ends of compressor, the pump with E pipe intercommunication.

In some embodiments, the sliding body can be controlled to slide according to the magnitude of the working medium pressure in the piston chamber a and the working medium pressure in the piston chamber B, when the pressure in the piston chamber a is greater than that in the piston chamber B, the sliding body can be pushed to move towards the piston chamber B to enable the D pipe to be communicated with the C pipe, the S pipe is communicated with the E pipe, when the pressure in the piston chamber a is less than that in the piston chamber B, the sliding body can be pushed to move towards the piston chamber a to enable the D pipe to be communicated with the E pipe, and the S pipe is communicated with the C pipe.

The evaporator comprises a first pipeline, a second pipeline and a third pipeline, wherein one end of the first pipeline is communicated with the pipe C, the other end of the first pipeline is communicated with the first end of the evaporator, one end of the second pipeline is communicated with the pipe S, the other end of the second pipeline is communicated with the first end of the evaporator, one end of the third pipeline is communicated with the pipe E, the other end of the third pipeline is communicated with the first end of the evaporator, a throttle valve is further arranged on the first pipeline, and the pump is arranged on the third pipeline; the second end of the evaporator is in communication with the suction end of the compressor.

In some embodiments, the refrigerant compressor further comprises a fourth pipeline, one end of the fourth pipeline is connected with the suction end of the compressor, the other end of the fourth pipeline is connected with the discharge end of the compressor, the check valve is arranged on the fourth pipeline, and the check valve allows the refrigerant to flow only in the direction from the end of the fourth pipeline connected with the suction end of the compressor to the other end connected with the discharge end of the compressor.

In some embodiments, the first communication tube is a capillary tube and the second communication tube is a capillary tube.

In some embodiments, the D tube can be in communication with the C tube and the S tube can be in communication with the E tube when the slider is slid into a first range of positions, the D tube can be in communication with the E tube and the S tube can be in communication with the C tube when the slider is slid into a second range of positions;

the valve body further comprises a first side wall located on one side of the reciprocating motion of the sliding body and a second side wall located on the other side of the reciprocating motion of the sliding body, the piston chamber A is formed between the sliding body and the first side wall, and the piston chamber B is formed between the sliding body and the second side wall.

In some embodiments, the valve body further comprises a third sidewall and a fourth sidewall, the D-tube communicates with the third sidewall, the C-tube, the S-tube, and the E-tube communicate with the fourth sidewall, respectively, and the third sidewall is opposite to the fourth sidewall;

the first side wall is opposite to the second side wall, one end of the first side wall is connected with the third side wall, the other end of the first side wall is connected with the fourth side wall, one end of the second side wall is connected with the third side wall, and the other end of the second side wall is connected with the fourth side wall.

In some embodiments, the slider includes a first piston disposed adjacent to the first sidewall with respect to the second piston, a second piston disposed adjacent to the second sidewall with respect to the first piston, and a seal portion between the first piston and the second piston, a first communication passage is provided between the seal portion and the first piston, a second communication passage is provided between the seal portion and the second piston, and a third communication passage is provided inside the seal portion and on a side toward the fourth sidewall.

In some embodiments, the seal portion is movable with the slider, the first piston, the second piston, and the seal portion move to communicate the D tube with the C tube through the first communication passage while communicating the S tube with the E tube through the third communication passage when the slider moves into the first position range, and move to communicate the D tube with the E tube through the second communication passage while communicating the S tube with the C tube through the third communication passage when the slider moves into the second position range.

In some embodiments, a sliding seat is further disposed inside the valve body, the sliding seat is fixedly disposed on the fourth side wall, a first channel, a second channel and a third channel are disposed on the sliding seat, the first channel is communicated with the C pipe, the second channel is communicated with the S pipe, the third channel is communicated with the E pipe, the sealing portion slides relatively on the sliding seat to communicate the first channel with the second channel or communicate the second channel with the third channel through the third communication channel, the first piston slides on one side of the sliding seat, and the second piston slides on the other side of the sliding seat.

In some embodiments, in a longitudinal section of the valve body, the third communication passage has a circular arc shape, the first communication passage has a rectangular shape, and the second communication passage has a rectangular shape.

In some embodiments, a throttling member is disposed in the S-tube, and the throttling member can throttle the working medium flowing through the S-tube during the process of opening the pump from closing the pump, so as to prevent all of the refrigerant pumped by the pump from flowing back to the E-tube through the S-tube.

In some embodiments, a positioning part is arranged in the S-pipe, the positioning part is arranged between the throttling part and the valve body, and the positioning part protrudes inwards in the radial direction to limit the movement direction of the throttling part towards the valve body; the throttling component is a throttling pipe.

In some embodiments, the pump is a liquid pump.

The dual-mode refrigeration system provided by the utility model has the following beneficial effects:

the four-way valve is arranged to comprise a first communicating pipe and a second communicating pipe, the first communicating pipe communicates a piston chamber A with a D pipe so as to lead pressure from the D pipe, the second communicating pipe communicates a piston chamber B with an S pipe so as to lead pressure from the S pipe, pressure difference is formed between two sides of a sliding body, the double-mode refrigeration system is effectively switched between modes through the pressure difference, a novel pressure difference driving type four-way valve is adopted to effectively replace a check valve and an electromagnetic valve which are in a parallel connection state in the prior art, compared with a conventional electromagnetic valve which is adopted in a fluorine pump heat pipe compression double mode in the prior art, the sliding body of the four-way valve is driven to move by the pressure difference generated by the operation of a fluorine pump or a compressor, electromagnetic driving is not needed, the electromagnetic valve is not opened by electrifying to start an electric signal, and compared with the structure of the conventional four-way valve, the four-way valve is not controlled to be switched by power-on or power-off, and an electromagnetic coil is not needed to drive the four-way valve, so that the waste of electric energy caused by the fact that the electromagnetic valve or the conventional four-way valve needs to be powered on for opening or closing control is avoided, the electric energy is saved, the service life of the control valve and the refrigeration system is effectively prolonged, and the reliability is improved; and system parts are reduced, an electromagnetic valve is cancelled, so that system control is simplified, reliability is improved, and design and control complexity of the controller are simplified.

Drawings

FIG. 1 is a system block diagram of a conventional prior art fluorine pump heat pipe compression dual mode refrigeration system;

FIG. 2 is a system configuration diagram of the compression mode of the dual mode refrigeration system employing the novel four-way valve of the present invention;

FIG. 3 is a system block diagram of the dual mode refrigeration system employing the novel four-way valve of the present invention in the fluorine pump mode;

fig. 4 is an internal structure diagram in the compression mode of the differential pressure drive four-way valve according to the present invention (the left piston chamber a is at a high pressure).

The reference numerals are represented as:

1. a valve body; 11. a piston chamber A; 12. a piston chamber B; 13. a first side wall; 14. a second side wall; 15. a third side wall; 16. a fourth side wall; 2. a slider; 21. a first piston; 22. a second piston; 23. a sealing part; 24. a first communicating passage; 25. a second communicating passage; 26. a third communicating passage; D. d, pipe; C. c, a pipe; s, S a tube; E. e, a pipe; 31. a first communication pipe; 32. a second communicating pipe; 4. a slide base; 41. a first channel; 42. a second channel; 43. a third channel; 5. a throttling member; 6. a compressor; 7. a condenser; 8. an evaporator; 9. a differential pressure driven four-way valve; 10. a one-way valve; 17. a pump; 101. a first pipeline; 102. a second pipeline; 103. a third pipeline; 104. a fourth pipeline; 18. a throttle valve.

Detailed Description

As shown in figure 1, when a heat pipe of a conventional fluorine pump and a compression refrigeration system share a condenser and an evaporator, the heat pipe and the compression refrigeration system belong to a parallel shared heat exchanger and a part of pipeline systems, a check valve A prevents refrigerant at the outlet of the fluorine pump from returning to a liquid inlet of the fluorine pump through a throttle valve, and an electromagnetic valve can prevent high-pressure refrigerant from pushing the fluorine pump and bypassing the throttle valve from the fluorine pump in a compression mode. Both the compressor and the fluorine pump are typically operated with only one of them, and very few are operating at the same time. The compressor, the condenser, the throttle valve and the evaporator are sequentially connected, and when the function of the fluorine pump heat pipe is increased, a bypass check valve B is additionally arranged at the compressor and flows to an exhaust port of the compressor from an air suction port of the compressor; a one-way valve A is additionally arranged between the throttling valve and the condenser and flows to the throttling valve from the condenser; and a solenoid valve and a fluorine pump are also connected between the outlet of the condenser and the inlet of the evaporator, and the solenoid valve is usually positioned at a liquid inlet of the fluorine pump.

Generally, two operation modes of a fluorine pump compression refrigeration system are a compression refrigeration mode and a fluorine pump refrigeration mode respectively, the two modes are generally switched in a transition season, generally, one mode can operate for a long time, and therefore the electromagnetic valve can be operated in a power-on state frequently, electric energy is wasted, and the service life and reliability of the electromagnetic valve are reduced.

Based on the consideration, the utility model adopts a novel pressure difference driving type four-way valve. As shown in the attached fig. 2 and 3, a compressor, a condenser, a four-way valve, a throttle valve and an evaporator of the novel system are connected in sequence, a one-way valve for bypass is additionally arranged at the compressor, and the one-way valve flows from an air suction port of the compressor to an air exhaust port of the compressor; the outlet of the condenser is connected to the D port of the four-way valve, the C port of the four-way valve is connected to the inlet of the throttle valve, and the E port of the four-way valve is connected to the liquid inlet of the fluorine pump; the outlet of the throttle valve, the S port of the four-way valve and the liquid outlet of the fluorine pump are connected to the inlet of the evaporator. The arrows in fig. 2 and 3 indicate the direction of refrigerant flow in the operating mode. The fluorine pump heat pipe system comprises a pump, an evaporator, a one-way valve and a condenser.

As shown in fig. 2, the refrigerant flow direction in the compression mode is: compressor discharge → condenser → four-way valve D → four-way valve C → throttle valve → evaporator → compressor suction.

As shown in fig. 3, the refrigerant flow direction in the fluorine pump mode is: the fluorine pump liquid outlet → the evaporator → the one-way valve → the condenser → the four-way valve D outlet → the four-way valve E outlet → the fluorine pump liquid inlet.

As shown in fig. 2-4, the present invention provides a dual mode refrigeration system comprising: compressor 6, condenser 7, evaporimeter 8, pressure differential drive formula four-way valve 9, check valve 10 and pump 17, and pressure differential drive formula four-way valve includes: a valve body 1, a slider 2, a D-tube D, C, a tube C, S, a tube S, E, a tube E, a first communication tube 31 and a second communication tube 32, the slider 2 being disposed in the valve body 1 and being slidable in the valve body 1, the D-tube D, the C-tube C, the S-tube S and the E-tube E being respectively communicated with the inside of the valve body 1, the valve body 1 including a piston chamber a11 on one side of the slider 2 reciprocating and a piston chamber B12 on the other side of the reciprocating, the first communication tube 31 having one end communicated with the D-tube D and the other end communicated with the piston chamber a11 to introduce pressure from the D-tube D into the piston chamber a11, the second communication tube 32 having one end communicated with the S-tube S and the other end communicated with the piston chamber B12 to introduce pressure from the S-tube S into the piston chamber B12;

d pipe D with condenser 7 intercommunication, C pipe C, S pipe S and E manage E and equally divide respectively with the one end intercommunication of evaporimeter 8, check valve 10 connects in parallel and sets up the both ends of compressor 6, pump 17 with E pipe E intercommunication.

When the compression mode shown in fig. 2 operates, the sliding body in the four-way valve moves rightwards under the action of the original pressure difference, and the DC communication and the SE communication are realized; when the compression mode stops operating, the internal sliding body keeps the original state. At the moment, the fluorine pump is started, the pressure of a liquid outlet of the fluorine pump is higher, the pressure of a piston chamber on the right side of the four-way valve is increased through the S port and the capillary tube, so that the sliding body is pushed to move leftwards until the sliding body moves to the leftmost end, the switching of the four-way valve is completed at the moment, and the system is the operation mode of the fluorine pump shown in the attached figure 3 at the moment.

Similarly, the operation mode of the fluorine pump shown in fig. 3 is switched to the compression refrigeration mode shown in fig. 2, and the pressure difference between the piston chambers at the two ends inside the four-way valve drives the sliding body inside the four-way valve to move, so that the operation mode is switched. After the operation modes are switched, the pressure difference of the piston chambers at the two ends of the four-way valve cannot be reversely changed, so that the position of the sliding body can be kept basically unchanged, and the stable operation of the system can be realized.

In some embodiments, the sliding body 2 can be controlled to slide according to the magnitude of the working medium pressure in the piston chamber a11 and the working medium pressure in the piston chamber B12, when the pressure in the piston chamber a11 is greater than that in the piston chamber B12, the sliding body 2 can be pushed to move towards the piston chamber B12 to enable the D pipe D to be communicated with the C pipe C, the S pipe S is communicated with the E pipe E, when the pressure in the piston chamber a11 is less than that in the piston chamber B12, the sliding body 2 can be pushed to move towards the piston chamber a11 to enable the D pipe D to be communicated with the E pipe E, and the S pipe S is communicated with the C pipe C.

The utility model sets four-way valve to include the first communicating pipe and the second communicating pipe, and the first communicating pipe connects the piston chamber A and the D pipe to lead the pressure from the D pipe, the second communicating pipe connects the piston chamber B and the S pipe to lead the pressure from the S pipe, and a pressure difference is formed between two sides of the sliding body, and the mode of the dual-mode refrigeration system is effectively switched directly through the pressure difference, compared with the conventional electromagnetic valve adopted in the fluorine pump heat pipe compression dual mode in the prior art, the electromagnetic valve is not required to be opened through electrifying and starting an electric signal, compared with the structure of the conventional four-way valve, the four-way valve is not required to be switched by electrifying or cutting off, and the four-way valve is not required to be driven by an electromagnetic coil, therefore, the waste of electric energy caused by the fact that the electromagnetic valve or the conventional four-way valve needs to be electrified for opening or closing control is avoided, the electric energy is saved, the service lives of the control valve and the refrigerating system are effectively prolonged, and the reliability is improved; and simplifies the design and control complexity of the controller.

The utility model adopts the pressure difference type novel four-way valve to replace the parallel structure of the one-way valve and the electromagnetic valve, simultaneously utilizes the pressure difference of the refrigerating system to directly drive the four-way valve, does not need the electromagnetic coil to drive the novel four-way valve, and has the advantages that: the design and control complexity of the controller is simplified; the reliability of the system operation is improved, and the electric energy is saved. The sliding body of the four-way valve is driven to move by pressure difference generated by the operation of the fluorine pump or the compressor, electromagnetic driving is not needed, so that the conversion of the operation mode is realized, the problems of electric energy consumption, service life reduction and reliability reduction caused by long-time electrifying and opening of the electromagnetic valve in a conventional fluorine pump heat pipe compression dual-mode refrigerating system are solved, and the problem that the electromagnetic four-way valve needs to be electrified and controlled is also solved.

As shown in fig. 2 and 3, the novel four-way valve is a differential pressure driving four-way valve, wherein pressure fluid at a D pipe and a S pipe of the novel four-way valve directly enters piston chambers at the left end and the right end of the four-way valve through corresponding pressure taking capillary tubes, and a sliding body inside the four-way valve is driven to move left and right by the pressure difference between the piston chambers at the two ends, so that the switching of the four-way valve is realized, an electromagnetic four-way valve coil is saved, and the structural design and control are simplified.

A D pipe is arranged on the middle section vertical to the central axis of the valve body, the pipe orifice is a D port, an S pipe is arranged on the middle section opposite to the D pipe of the valve body, and the pipe orifice is an S port; the left side and the right side of the S pipe are provided with a pipe C and a pipe E, and the pipe openings are respectively a port C and a port E. Generally, the four tubes are in the same plane, which generally passes through the central axis of the valve body; the four pipes are not necessarily straight pipes, and can be made into U-shaped pipes, flared pipes, bent pipes and the like according to requirements; the through holes of the valve body and the four pipes are matched with each other are outward flanged holes generally, and the four pipes are inserted into the valve body and are firmly welded with the valve body.

The C pipe, the S pipe and the E pipe of the four-way valve are inserted into the valve body, the inserted pipe openings do not exceed the surface of the sliding seat, and the flush surface of the sliding seat is beneficial to the sliding body of the four-way valve to slide left and right on the surface. The three pipes are inserted into corresponding through holes of the sliding base and are in interference fit usually, and therefore fluid in the four-way valve is prevented from being mixed and communicated. The D pipe of the four-way valve is inserted into the valve body, and the pipe orifice does not exceed the top end of the sliding body, so that the sliding body is prevented from moving left and right.

In some embodiments, the system further comprises a first pipeline 101, a second pipeline 102 and a third pipeline 103, wherein one end of the first pipeline 101 is communicated with the pipe C, the other end of the first pipeline is communicated with the first end of the evaporator 8, one end of the second pipeline 102 is communicated with the pipe S, the other end of the second pipeline is communicated with the first end of the evaporator 8, one end of the third pipeline 103 is communicated with the pipe E, the other end of the third pipeline is communicated with the first end of the evaporator 8, a throttle valve 18 is further arranged on the first pipeline 101, and the pump 17 is arranged on the third pipeline 103; a second end of the evaporator 8 communicates with a suction end of the compressor 6. According to the utility model, the C pipe, the S pipe and the E pipe can be effectively connected to the evaporator through the arrangement of the first pipeline, the second pipeline and the third pipeline, the throttle valve is arranged on the first pipeline, the pump is arranged on the third pipeline, so that the D pipe is communicated with the C pipe in a compressor mode, namely, the refrigerant is throttled and depressurized by the throttle valve on the first pipeline and then is conveyed into the evaporator, the pump communicated with the E pipe is closed in the mode, and the S pipe is communicated with the E pipe and does not circulate the refrigerant; and in the fluorine pump mode, the pipe D is communicated with the pipe E, the refrigerant is pumped into the evaporator through the pump of the third pipeline and then returns to the pump through the pipe D, the first communication pipeline communicated with the pipe C is closed in the mode, and the compressor is closed.

In some embodiments, the refrigerant compressor further comprises a fourth pipeline 104, one end of the fourth pipeline 104 is connected to the suction end of the compressor 6, the other end of the fourth pipeline is connected to the discharge end of the compressor 6, the check valve 10 is disposed on the fourth pipeline 104, and the check valve 10 allows the refrigerant to flow only from the end of the fourth pipeline 104 connected to the suction end of the compressor 6 to the other end connected to the discharge end of the compressor 6. The utility model also enables the refrigerant to flow through the fourth pipeline and the check valve 10 without flowing through the compressor in the fluorine pump mode through the arrangement of the fourth pipeline, so that the refrigerant circulation in the fluorine pump mode is completed, and the check valve is used for preventing the refrigerant from returning to the suction port of the compressor from the exhaust port of the compressor through the fourth pipeline when the compressor is started, thereby avoiding the refrigerant from forming an effective circulation.

In some embodiments, when the slider 2 is slid into a first range of positions, the D tube D can be in communication with the C tube C, and the S tube S can be in communication with the E tube E, and when the slider 2 is slid into a second range of positions, the D tube D can be in communication with the E tube E, and the S tube S can be in communication with the C tube C;

the valve body 1 further includes a first side wall 13 on one side of the reciprocating motion of the slider 2 and a second side wall 14 on the other side of the reciprocating motion, the piston chamber a11 is formed between the slider 2 and the first side wall 13, and the piston chamber B12 is formed between the slider 2 and the second side wall 14.

This is a preferred structural form of the sliding body and the valve body of the present invention, as shown in fig. 4, the sliding body moves to the right to the first position range and moves to the left to the second position range, the valve body is preferably a cylindrical or rectangular main body structure, the left end of the valve body is a first side wall, the right end of the valve body is a second side wall, the space between the first side wall and the first piston (left space) is a piston chamber a, the space between the second side wall and the second piston (right space) is a piston chamber B, and the movement of the sliding body can be controlled by the communication pressure between the left and right spaces, thereby achieving the purpose of controlling the mode switching of the dual-mode refrigeration system.

In some embodiments, the first connection pipe 31 is a capillary tube, and the second connection pipe 32 is also a capillary tube. The optimal structure of the two communicating pipes is that the corresponding pressure can be introduced from the D pipe or the S pipe through the structure of the capillary pipe, but the working medium with overlarge flow can not enter the piston chamber, so that the movement amount of the sliding body is overlarge, and the sliding body can not be effectively switched left and right.

A capillary tube A (a first connecting tube 31) is led out from the side wall of the tube D, and the other end of the capillary tube A is connected to the left end cover of the four-way valve and is respectively welded firmly; and a capillary tube B (a second communicating tube 32) is led out from the side wall of the S tube, and the other end of the capillary tube B is connected to the right end cover of the four-way valve and is respectively welded firmly. The capillary tube A is communicated with the tube D and the piston chamber A, and the capillary tube B is communicated with the tube S and the piston chamber B.

In some embodiments, the valve body 1 further comprises a third side wall 15 and a fourth side wall 16, the D pipe D communicates with the third side wall 15, the C pipe C, the S pipe S and the E pipe E respectively communicate with the fourth side wall 16, and the third side wall 15 is opposite to the fourth side wall 16;

the first side wall 13 is opposite to the second side wall 14, one end of the first side wall 13 is connected to the third side wall 15, the other end of the first side wall is connected to the fourth side wall 16, one end of the second side wall 14 is connected to the third side wall 15, and the other end of the second side wall is connected to the fourth side wall 16.

The valve body is a further preferable structure form of the valve body, the D pipe can be respectively arranged on the third side wall and the fourth side wall, and the C \ S \ E pipe is arranged on the fourth side wall, so that a preferable pipeline connection form of the four-way valve is formed.

In some embodiments, the slider 2 includes a first piston 21, a second piston 22, and a sealing portion 23, the first piston 21 is disposed close to the first side wall 13 with respect to the second piston 22, the second piston 22 is disposed close to the second side wall 14 with respect to the first piston 21, the sealing portion 23 is located between the first piston 21 and the second piston 22, a first communication passage 24 is disposed between the sealing portion 23 and the first piston 21, a second communication passage 25 is disposed between the sealing portion 23 and the second piston 22, and a third communication passage 26 is disposed inside the sealing portion 23 and on a side facing the fourth side wall 16. The sliding body is a preferable structure form of the sliding body, a piston chamber A can be formed between the first piston and the first side wall, and the working medium in the piston chamber A acts on the first piston to form the movement of the first piston; the second piston can form a piston chamber B with the second side wall, and the working medium in the piston chamber B acts on the second piston to form the motion of the second piston; the effect of sealing part lies in carrying out the intercommunication to S and C or S and E intercommunication, and C or E that do not communicate with S then communicate with D, and the third intercommunication passageway through sealing part realizes C and S intercommunication or S and E intercommunication, and sealing part keeps apart D pipe and prevents D and third intercommunication passageway 26 intercommunication for D can communicate with C or with E.

The sliding body of the four-way valve is divided into three parts, the middle part is arched, and the left end and the right end are pistons. The left side and the right side of the arch are provided with through holes in the vertical direction, and the two through holes mainly enable the D pipe to be communicated with the C pipe or the E pipe (DC communication or DE communication); and the lower end of the middle arch center is provided with a reversed crescent empty groove which mainly has the functions of communicating the S pipe with the C pipe or the S pipe with the E pipe (CS communication or ES communication), and not communicating the crescent empty groove with the region of the D pipe. Pistons are respectively arranged at the left end and the right end of the sliding body, the outer diameter of each piston is matched and sealed with the inner diameter of the valve body and can move left and right, and the end covers at the two ends of the valve body and the sliding seat limit the position of the piston moving left and right. The left end cover is close to the pipe C, and the right end cover is close to the pipe E.

In some embodiments, the seal portion 23 is movable with the slider 2, and when the slider 2 moves into the first position range, the first piston 21, the second piston 22, and the seal portion 23 move to communicate the D tube D with the C tube C through the first communication passage 24 while communicating the S tube S with the E tube E through the third communication passage 26, and when the slider 2 moves into the second position range, the first piston 21, the second piston 22, and the seal portion 23 move to communicate the D tube D with the E tube E through the second communication passage 25 while communicating the S tube S with the C tube C through the third communication passage 26. This is a preferable configuration of the seal portion of the present invention, and the movement thereof to the first position range enables communication between S and E through the third communication passage, and communication between the D-pipe and the C-pipe is performed through the first communication passage; and can communicate S and C through the third intercommunication passageway when moving to the second position within range, communicate through the second intercommunication passageway between D pipe and the E pipe to the realization is carried out 4 pipelines through three intercommunication passageways on the sliding body and is carried out the intercommunication between two by two, and the switching between the intercommunication.

In some embodiments, a sliding seat 4 is further disposed inside the valve body 1, the sliding seat 4 is fixedly disposed on the fourth side wall 16, and a first channel 41, a second channel 42 and a third channel 43 are disposed on the sliding seat 4, the first channel 41 is communicated with the C pipe C, the second channel 42 is communicated with the S pipe S, the third channel 43 is communicated with the E pipe E, the sealing portion 23 slides relatively on the sliding seat 4 to communicate the first channel 41 with the second channel 42 or communicate the second channel 42 with the third channel 43 through the third communication channel 26, the first piston 21 slides on one side of the sliding seat 4, and the second piston 22 slides on the other side of the sliding seat 4. The four-way valve is a further preferable structure form of the four-way valve, the sealing part can be arranged on the four-way valve in a sliding way through the arrangement of the sliding seat, and three channels on the four-way valve are used for being communicated with C \ S \ E respectively.

In some embodiments, the third communication passage 26 has a circular arc shape, the first communication passage 24 has a rectangular shape, and the second communication passage 25 has a rectangular shape in a longitudinal section of the valve body 1. This is the preferred shape of the three communicating channels of the present invention.

In some embodiments, a throttling member 5 is disposed in the S-pipe S, and the throttling member 5 can throttle the working medium flowing through the S-pipe S during the process of opening the pump 17 from closing so as to prevent all of the refrigerant pumped by the pump 17 from flowing back to the E-pipe E through the S-pipe S. According to the utility model, through the arrangement of the throttling component in the S pipe, when the first position is switched to the second position, the working medium in the E pipe can be prevented from directly flowing back to the E pipe from the S pipe through the third communication channel, so that the fluid can not be pumped into the refrigeration system to form circulation, and the reliability of operation switching is improved.

A throttling component in the S port of the four-way valve or a capillary tube is adopted to replace a pipe port where the S port is located, so that safe operation of a pump (preferably a liquid pump or a fluorine pump) under mode switching can be guaranteed, and pressure lift generated by the pump at the moment is basically consumed on the throttling component in the pipe where the S port is located. When the mode is completely switched, most of high-pressure liquid at the outlet of the pump flows to the evaporator, and only a small amount of high-pressure liquid returns to the liquid inlet of the pump through the S port.

In some embodiments, a positioning member is disposed in the S-pipe S, the positioning member is disposed between the throttling member 5 and the valve body 1, and the positioning member protrudes inward in a radial direction to limit a moving direction of the throttling member 5 toward the valve body 1; the throttling component 5 is a throttling pipe. The utility model also can prevent the throttling component from entering the valve body to influence the movement of components such as a sliding body in the valve body through the arrangement of the positioning component. The position of the S pipe, which is out of the capillary pipe, is embedded with a throttling short pipe (the function is to establish pressure difference and effectively switch), the upper end position of the S pipe, which is close to the throttling short pipe, is pressed with a positioning ring, the positioning ring protrudes towards the inside of the S pipe to prevent the throttling short pipe from moving towards the valve body, and the capillary pipe orifice inserted into the S pipe can prevent the throttling short pipe from sliding out of the S port.

In an alternative embodiment, the whole section of the S-pipe S is a throttle pipe structure, and is fixedly connected with the valve body 1 (not shown). The difference with the main embodiment is that the pipeline where the S opening is located is changed into a throttle pipe or a capillary pipe, meanwhile, the capillary pipe B is not directly connected with the S pipe, the pipe opening of the capillary pipe B is directly connected to the valve body and is firmly welded, and the processing technology is the same as that of the S pipe connected to the valve body. The other structural designs of the four-way valve are the same as those of the attached figures 2 and 3.

The present invention also provides a method of controlling a dual mode refrigeration system as described in any of the preceding claims, comprising:

a detection step of detecting an outdoor temperature T;

a judging step of judging T and a preset temperature T_{Preset of}The relationship between;

control step, when T > T_{Preset of}When the pressure sensor detects the pressure, the compressor 6 is controlled to be started, the pump 17 is controlled to be closed, and the pressure sensor controlsThe dual-mode refrigeration system enters a compressor mode, and refrigerant is compressed by the compressor 6 and then returns to the compressor after sequentially passing through the condenser 7, the D pipe, the C pipe and the evaporator 8;

when T is less than T_{Preset of}When the refrigerant passes through the evaporator 8, the one-way valve 10, the condenser 7, the pipe D and the pipe E, the refrigerant returns to the pump 17 in sequence after being driven by the pump 17.

The utility model directly carries out effective switching between modes of the dual-mode refrigeration system through pressure difference, effectively replaces a one-way valve and an electromagnetic valve in a parallel connection state in the prior art by adopting the novel pressure difference driving type four-way valve, and drives a sliding body of the four-way valve to move by depending on the pressure difference generated by the operation of a fluorine pump or a compressor compared with the conventional electromagnetic valve adopted in the fluorine pump heat pipe compression dual-mode in the prior art without electromagnetic driving and opening the electromagnetic valve by electrifying and starting an electric signal, and controls the four-way valve to switch by electrifying or cutting off the power compared with the structure of the conventional four-way valve without driving the four-way valve by an electromagnetic coil, therefore, the waste of electric energy caused by the fact that the electromagnetic valve or the conventional four-way valve needs to be electrified for opening or closing control is avoided, the electric energy is saved, the service lives of the control valve and the refrigerating system are effectively prolonged, and the reliability is improved; and system parts are reduced, an electromagnetic valve is cancelled, so that system control is simplified, reliability is improved, and design and control complexity of the controller are simplified.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims

1. A dual mode refrigeration system characterized by: the method comprises the following steps:

the compressor comprises a compressor (6), a condenser (7), an evaporator (8), a differential pressure driving type four-way valve (9), a one-way valve (10) and a pump (17), wherein the differential pressure driving type four-way valve (9) comprises a valve body (1), a sliding body (2), a D pipe (D), a C pipe (C), an S pipe (S), an E pipe (E), a first communicating pipe (31) and a second communicating pipe (32), the sliding body (2) is arranged in the valve body (1) and can slide in the valve body (1), the D pipe (D), the C pipe (C), the S pipe (S) and the E pipe (E) are respectively communicated with the interior of the valve body (1), the valve body (1) comprises a piston chamber A (11) located on one side of the reciprocating motion of the sliding body (2) and a piston chamber B (12) located on the other side of the reciprocating motion, one end of the first communicating pipe (31) is communicated with the D pipe (D), The other end is communicated with the piston chamber A (11) to introduce pressure from the D pipe (D) into the piston chamber A (11), one end of the second communication pipe (32) is communicated with the S pipe (S), and the other end is communicated with the piston chamber B (12) to introduce pressure from the S pipe (S) into the piston chamber B (12);

d pipe (D) with condenser (7) intercommunication, C pipe (C), S pipe (S) and E pipe (E) equally divide respectively with the one end intercommunication of evaporimeter (8), check valve (10) parallelly connected the setting is in the both ends of compressor (6), pump (17) with E pipe (E) intercommunication.

2. A dual mode refrigeration system as set forth in claim 1 wherein:

the sliding body (2) can be controlled to slide according to the magnitude of working medium pressure in the piston chamber A (11) and working medium pressure in the piston chamber B (12), when the pressure in the piston chamber A (11) is greater than that in the piston chamber B (12), the sliding body (2) can be pushed to move towards the piston chamber B (12) to enable the D pipe (D) to be communicated with the C pipe (C), the S pipe (S) is communicated with the E pipe (E), when the pressure in the piston chamber A (11) is less than that in the piston chamber B (12), the sliding body (2) can be pushed to move towards the piston chamber A (11) to enable the D pipe (D) to be communicated with the E pipe (E), and the S pipe (S) is communicated with the C pipe (C).

3. A dual mode refrigeration system as set forth in claim 1 wherein:

the evaporator is characterized by further comprising a first pipeline (101), a second pipeline (102) and a third pipeline (103), wherein one end of the first pipeline (101) is communicated with the pipe C, the other end of the first pipeline is communicated with the first end of the evaporator (8), one end of the second pipeline (102) is communicated with the pipe S, the other end of the second pipeline is communicated with the first end of the evaporator (8), one end of the third pipeline (103) is communicated with the pipe E, the other end of the third pipeline is communicated with the first end of the evaporator (8), a throttle valve (18) is further arranged on the first pipeline (101), and the pump (17) is arranged on the third pipeline (103); the second end of the evaporator (8) is communicated with the suction end of the compressor (6).

4. A dual mode refrigeration system as set forth in claim 1 wherein:

still include fourth pipeline (104), the one end of fourth pipeline (104) with the suction end of compressor (6) is connected, the other end with the exhaust end of compressor (6) is connected, check valve (10) set up on fourth pipeline (104), just check valve (10) allow the refrigerant flow direction only for follow fourth pipeline (104) with the one end flow direction that the suction end of compressor (6) is connected with the other end that the exhaust end of compressor (6) is connected.

5. A dual mode refrigeration system as set forth in claim 1 wherein:

the first communicating pipe (31) is a capillary pipe, and the second communicating pipe (32) is also a capillary pipe.

6. A dual mode refrigeration system as set forth in claim 1 wherein:

when the sliding body (2) slides to a first position range, the D pipe (D) can be communicated with the C pipe (C), the S pipe (S) can be communicated with the E pipe (E), when the sliding body (2) slides to a second position range, the D pipe (D) can be communicated with the E pipe (E), and the S pipe (S) can be communicated with the C pipe (C);

the valve body (1) further comprises a first side wall (13) located on one side of the reciprocating motion of the sliding body (2) and a second side wall (14) located on the other side of the reciprocating motion, the piston chamber A (11) is formed between the sliding body (2) and the first side wall (13), and the piston chamber B (12) is formed between the sliding body (2) and the second side wall (14).

7. A dual mode refrigeration system as set forth in claim 6 wherein:

the valve body (1) further comprises a third side wall (15) and a fourth side wall (16), the D pipe (D) is communicated with the third side wall (15), the C pipe (C), the S pipe (S) and the E pipe (E) are respectively communicated with the fourth side wall (16), and the third side wall (15) is opposite to the fourth side wall (16);

the first side wall (13) is opposite to the second side wall (14), one end of the first side wall (13) is connected with the third side wall (15), the other end of the first side wall is connected with the fourth side wall (16), one end of the second side wall (14) is connected with the third side wall (15), and the other end of the second side wall is connected with the fourth side wall (16).

8. A dual mode refrigeration system as set forth in claim 7 wherein:

the sliding body (2) comprises a first piston (21), a second piston (22) and a sealing portion (23), the first piston (21) is arranged close to the first side wall (13) relative to the second piston (22), the second piston (22) is arranged close to the second side wall (14) relative to the first piston (21), the sealing portion (23) is located between the first piston (21) and the second piston (22), a first communication channel (24) is arranged between the sealing portion (23) and the first piston (21), a second communication channel (25) is arranged between the sealing portion (23) and the second piston (22), and a third communication channel (26) is arranged in the sealing portion (23) and faces one side of the fourth side wall (16).

9. A dual mode refrigeration system as set forth in claim 8 wherein:

the sealing part (23) is movable with the sliding body (2), when the sliding body (2) moves into the first position range, the first piston (21), the second piston (22) and the seal portion (23) move to communicate the D-pipe (D) with the C-pipe (C) through the first communication passage (24), while the S-pipe (S) is communicated with the E-pipe (E) through the third communication passage (26), when the slider (2) moves into the second position range, the first piston (21), the second piston (22), and the seal portion (23) move to communicate the D-pipe (D) with the E-pipe (E) through the second communication passage (25), while communicating the S tube (S) with the C tube (C) through the third communication passage (26).

10. A dual mode refrigeration system as set forth in claim 8 wherein:

a sliding seat (4) is further arranged in the valve body (1), the sliding seat (4) is fixedly arranged on the fourth side wall (16), and the sliding seat (4) is provided with a first channel (41), a second channel (42) and a third channel (43), the first passage (41) communicating with the C pipe (C), the second passage (42) communicating with the S pipe (S), the third channel (43) communicates with the E-tube (E), the sealing portion (23) slides relatively on the slide (4), to communicate the first passage (41) with the second passage (42) or to communicate the second passage (42) with the third passage (43) through the third communication passage (26), the first piston (21) is located on one side of the sliding seat (4) for sliding, the second piston (22) is located on the other side of the slide (4) for sliding.

11. A dual mode refrigeration system as set forth in claim 8 wherein:

in a longitudinal section of the valve body (1), the third communication channel (26) is in the shape of a circular arc, and/or the first communication channel (24) is in the shape of a rectangle, and/or the second communication channel (25) is also in the shape of a rectangle.

12. A dual mode refrigeration system as set forth in any one of claims 1-11 wherein:

a throttling part (5) is arranged in the S pipe (S), and the throttling part (5) can throttle working medium flowing through the S pipe (S) in the process that the pump (17) is switched from closed to open so as to prevent all refrigerant pumped by the pump (17) from flowing back to the E pipe (E) through the S pipe (S).

13. A dual mode refrigeration system as set forth in claim 12 wherein:

a positioning part is arranged in the S pipe (S), the positioning part is arranged between the throttling part (5) and the valve body (1), and the positioning part protrudes inwards along the radial direction so as to limit the throttling part (5) towards the movement direction of the valve body (1); the throttling component (5) is a throttling pipe.

14. A dual mode refrigeration system as set forth in any one of claims 1-11 wherein:

the pump (17) is a liquid pump.