CN111255687A

CN111255687A - Compressor and refrigerating system

Info

Publication number: CN111255687A
Application number: CN201811457035.2A
Authority: CN
Inventors: 廖四清; 曾令华; 王小龙; 区永东; 杨宇飞
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2018-11-30
Filing date: 2018-11-30
Publication date: 2020-06-09

Abstract

The invention discloses a compressor and a refrigerating system, wherein the compressor comprises: the air cylinder comprises a first air cylinder, a second air cylinder and a variable volume structure. Through the cooperation of the first cylinder, the second cylinder and the variable-capacity structure, the compressor can be controlled to operate a single-stage compression mode or a two-stage compression belt intermediate cooling mode, and along with the switching of the compression mode, the capacity of the compressor is changed, and V2 and V1 satisfy the relation of the ratio: V2/V1 is more than or equal to 40% and less than or equal to 70%, optimal energy efficiency exertion can be guaranteed during the two-stage compression mode of the compressor, and meanwhile, the partial load operation has the optimal variable capacity ratio, so that the seasonal energy efficiency effect of the constant-speed compressor can be improved.

Description

Compressor and refrigerating system

Technical Field

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

Background

In the related technology, when the compressor operates in two-stage compression, intermediate air injection is performed, but intermediate cooling is not performed, the capacity ratio of two cylinders of a common compressor is designed to be 70-90%, the performance is better, the effect of reducing the secondary exhaust temperature of the compressor is not obvious, the capacity ratio is in the range of 70-90%, and the compressor is used for improving the energy efficiency in the season by constant speed and variable capacity and is not in the range of the better capacity ratio.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. To this end, an object of the present invention is to provide a compressor, which can control the compressor to operate in a single-stage compression mode or a two-stage compression band intermediate cooling mode, and also can improve the seasonal energy efficiency of a constant-speed compressor.

The invention further provides a refrigerating system.

The compressor according to the present invention includes: the air cylinder comprises a first air cylinder, a second air cylinder and a variable volume structure. The first cylinder is provided with a first air inlet and a first air outlet, the second cylinder is provided with a second air inlet and a second air outlet, the capacity of the first cylinder is V1, and the capacity of the second cylinder is V2; the variable-volume structure is arranged for controlling the first cylinder to operate so as to compress the refrigerant entering the first cylinder or unload the first cylinder; the compressor is provided with a single-stage compression mode and a double-stage compression belt intercooling mode, when the compressor is in the single-stage compression mode, the first cylinder is controlled by the variable-volume structure to unload, the second cylinder operates, when the compressor is in the double-stage compression belt intercooling mode, the first cylinder is controlled by the variable-volume structure to operate, the second cylinder also operates, the refrigerant sucked by the first air inlet is discharged from the first air outlet after being compressed by the first cylinder, the discharged refrigerant is sucked by the second air inlet after being cooled and compressed in the second cylinder, and the refrigerant subjected to secondary compression is discharged from the second air outlet, wherein the V2 and the V1 satisfy a ratio relation: V2/V1 is more than or equal to 40% and less than or equal to 70%.

According to the compressor provided by the invention, the first cylinder, the second cylinder and the variable volume structure are matched, the compressor can be controlled to operate a single-stage compression mode or a double-stage compression belt intermediate cooling mode, and the capacity of the compressor is changed along with the switching of the compression mode, so that V2 and V1 satisfy the relation of ratio: V2/V1 is more than or equal to 40% and less than or equal to 70%, optimal energy efficiency exertion can be guaranteed during the two-stage compression mode of the compressor, and meanwhile, the partial load operation has the optimal variable capacity ratio, so that the seasonal energy efficiency effect of the constant-speed compressor can be improved.

In some examples of the invention, the first cylinder has a first slide groove and a slide slidable in the first slide groove, and the back of the slide is provided with a back pressure chamber, and the first cylinder is unloaded by selectively connecting the back pressure chamber with high pressure to operate the first cylinder or selectively connecting low pressure to operate the first cylinder.

In some examples of the invention, the compressor further comprises: a four-way valve having a first port connected to the first exhaust port, a second port connected to the first intake port, a third port connected to a reservoir of the compressor, and a fourth port connected to the second intake port, wherein the first port is communicated with the second port and the third port is communicated with the fourth port, or the first port is communicated with the fourth port and the second port is communicated with the third port.

In some examples of the present invention, the back pressure chamber of the vane back communicates with the second suction port.

In some examples of the invention, the compressor further comprises: the first interface of three-way valve with the backpressure chamber intercommunication at gleitbretter back, the second interface of three-way valve with blast pipe intercommunication on the casing of compressor, the third interface of three-way valve with the reservoir intercommunication of compressor, the first interface of three-way valve can selectively communicate the second interface with the third interface.

In some examples of the present invention, a reservoir of the compressor is connected to the first suction port and the second suction port, respectively, a first opening and closing valve is provided between the second suction port and the reservoir, and the first discharge port and the back pressure chamber at the back of the vane are each connected to the second suction port without passing through the first opening and closing valve.

In some examples of the invention, the compressor further comprises: the first interface of the three-way valve is connected with the first exhaust port, the second interface of the three-way valve is connected with the second air suction port, the third interface of the three-way valve is connected with the first air suction port, the liquid storage device of the compressor is connected with the first air suction port, and the second interface can be selectively communicated with one of the first interface and the third interface.

In some examples of the invention, the compressor is a fixed speed compressor.

In some examples of the invention, the compressor has a two-step capacitor configuration.

The refrigeration system comprises the compressor.

In some examples of the present invention, the refrigeration system includes an outdoor heat exchanger, an indoor heat exchanger, and an injection device connected between the indoor heat exchanger and the outdoor heat exchanger, where the injection device includes an injection port, and the injection port is used for mixing a low-temperature refrigerant injected by the injection device with a high-temperature refrigerant discharged by the first exhaust port, so that the refrigerant discharged by the first exhaust port is cooled, and the refrigerant enters the second suction port after being cooled.

In some examples of the invention, the injection device is a gas-liquid separator or a first heat exchanger.

In some examples of the invention, the refrigeration system further comprises: and the second heat exchanger is used for cooling the refrigerant which is discharged through the first exhaust port and enters the second suction port.

In some examples of the present invention, an oil separator is provided between the first exhaust port and the injection device, and a throttle device is provided between the oil separator and the second suction port.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

FIG. 1 is a wiring diagram of a two-stage capacitor structure carried by a compressor according to an embodiment of the present invention;

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

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

FIG. 4 is a schematic diagram of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 5 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 6 is a schematic diagram of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 7 is a schematic diagram of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 8 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 9 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 10 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 11 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 12 is a schematic view of another embodiment of a refrigeration system according to an embodiment of the present invention;

FIG. 13 is a schematic diagram of another embodiment of a refrigeration system according to an embodiment of the present invention.

Reference numerals:

a compressor 10;

a first cylinder 1; a first air intake port 11; a first exhaust port 12; a first vane groove 13; a slide 14;

a second cylinder 2; a second air inlet 21; a second exhaust port 22;

a varactor structure 3;

a four-way valve 4; the first valve port 41; a second valve port 42; a third port 43; a fourth valve port 44;

a liquid reservoir 5;

a first three-way valve 6; a first interface 61; a second interface 62; a third interface 63; an exhaust pipe 64;

a first opening/closing valve 7; a third heat exchanger 8;

a second three-way valve 9; a first interface 91; a second interface 92; a third interface 93;

a refrigeration system 20;

an outdoor heat exchanger 201; an indoor heat exchanger 202; an injection device 203; an injection port 204; a second heat exchanger 205; an oil separator 206; a throttle device 207.

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 present invention is described below with reference to fig. 1 to 13.

As shown in fig. 1 to 13, a compressor 10 according to an embodiment of the present invention includes: a first cylinder 1, a second cylinder 2 and a variable volume structure 3. The first cylinder 1 may have a first intake port 11 and a first exhaust port 12, the second cylinder 2 may have a second intake port 21 and a second exhaust port 22, the capacity of the first cylinder 1 is V1, and the capacity of the second cylinder 2 is V2. The variable volume structure 3 may be configured to control the operation of the first cylinder 1 to compress the refrigerant entering the first cylinder 1 or unload the first cylinder 1, that is, the variable volume structure 3 may control the first cylinder 1 to operate, and may also control the first cylinder 1 not to operate, and it may also be understood that the variable volume structure 3 may switch the capacity of the first cylinder 1 between two capacities, i.e., 0 and V1.

The compressor 10 can have a single-stage compression mode and a two-stage compression band intermediate cooling mode, when the compressor 10 is in the single-stage compression mode, the first cylinder 1 is controlled to be unloaded by the variable-volume structure 3, and the second cylinder 2 operates, at this time, the first cylinder 1 does not work, the second cylinder 2 works, and the refrigerant is compressed only once through the second cylinder 2.

When the compressor 10 is in the two-stage compression band intercooling mode, the first cylinder 1 is controlled by the variable-volume structure 3 to operate, the second cylinder 2 also operates, the refrigerant sucked in from the first air inlet 11 is compressed by the first cylinder 1 and then discharged from the first exhaust port 12, the discharged refrigerant is cooled and then sucked in by the second air inlet 21 and compressed in the second cylinder 2, the secondarily compressed refrigerant is discharged from the second exhaust port 22, and the ratio relation between V2 and V1 is satisfied: V2/V1 is more than or equal to 40% and less than or equal to 70%.

The structure of the variable volume structure 3 is not limited, and the variable volume structure 3 may be any type of variable volume structure 3, when the compressor 10 is in a two-stage compression band intercooling mode, the compressor 10 is in full-load operation at this time, intercooling can improve the energy efficiency of the compressor 10, and the temperature of the refrigerant discharged from the first exhaust port 12 is reduced after being cooled, and then the refrigerant with the reduced temperature flows into the second cylinder 2 to be compressed.

In some embodiments of the present invention, the compressor 10 may be configured as a fixed speed compressor 10, the preferred capacity ratio of the two-stage compressor 10 is preferably within a range of 40% V2/V1% to 70% when compared to the capacity ratio without intercooling, the capacity ratio is such that when the compressor 10 is in the single-stage compression mode, the compressor 10 is in partial load operation, the seasonal energy efficiency of the compressor 10 is greatly increased, and the ratio of the first cylinder 1 to the second cylinder 2 is 40% -70%, which is exactly the cylinder ratio at which the seasonal energy efficiency of the fixed speed compressor 10 is increased. Therefore, by providing the variable capacity structure 3, the compressor 10 can be controlled to operate the single-stage compression mode or the two-stage compression band intermediate cooling mode, and the ratio relation between V2 and V1 is satisfied: V2/V1 is more than or equal to 40% and less than or equal to 70%, and the compressor 10 can be ensured to have optimal energy efficiency, so that the seasonal energy efficiency of the constant-speed compressor 10 can be improved. When the compressor 10 operates in the cooling operation mode, the intercooling is to dissipate heat to the external environment to improve the energy efficiency and reduce the exhaust temperature, and when the compressor 10 operates in the heating operation mode, the intercooling is to dissipate heat to a liquid refrigerant in a flash evaporator or cool and spray the liquid refrigerant with the economizer and the refrigerant discharged from the first exhaust port 12 into the second cylinder 2, so that the heat is not dissipated to the external environment, and the heating quantity is not lost.

Therefore, through the cooperation of the first cylinder 1, the second cylinder 2 and the variable-capacity structure 3, the compressor 10 can be controlled to operate a single-stage compression mode or a two-stage compression belt intercooling mode, and as the compression mode is switched, the capacity of the compressor 10 is changed, and the ratio relation between V2 and V1 is satisfied: V2/V1 is more than or equal to 40% and less than or equal to 70%, optimal energy efficiency exertion can be guaranteed when the compressor 10 is in the two-stage compression mode, and meanwhile, partial load operation also has the optimal variable capacity ratio, so that the seasonal energy efficiency effect of the constant-speed compressor 10 can be improved.

In some embodiments of the present invention, as shown in fig. 2 to 13, the compressor 10 may be configured as a rotary compressor 10, the first cylinder 1 may have a first vane groove 13 and a vane 14 slidable in the first vane groove 13, and a back of the vane 14 may be provided with a back pressure chamber, and the first cylinder 1 may be unloaded by selectively communicating a high pressure to the back pressure chamber to operate the first cylinder 1 or selectively communicating a low pressure to the back pressure chamber. Wherein, the back of the sliding piece 14 is provided with a back pressure cavity with only one connecting port, when the connecting port of the back pressure cavity is connected with high pressure (the high pressure is only equal to or higher than the pressure of the first exhaust port 12), the first cylinder 1 works, when the connecting port of the back pressure cavity is connected with low pressure (for example, the first exhaust port 11 is the low pressure), the first cylinder 1 is unloaded. Wherein the pressure change in the second cylinder 2 can be achieved by communicating the back pressure chamber with the second suction port 21.

In some embodiments of the present invention, as shown in fig. 2, 3, 5, 6, 7, 8, 11, and 13, the compressor 10 may further include: and a four-way valve 4, wherein the four-way valve 4 has a first port 41, a second port 42, a third port 43 and a fourth port 44, the first port 41 is connected to the first exhaust port 12, the second port 42 is connected to the first intake port 11, the third port 43 is connected to the reservoir 5 of the compressor 10, and the fourth port 44 is connected to the second intake port 21, wherein the first port 41 is communicated with the second port 42 and the third port 43 is communicated with the fourth port 44, or the first port 41 is communicated with the fourth port 44 and the second port 42 is communicated with the third port 43.

In some embodiments of the present invention, as shown in fig. 2, 4, 5, 6, 7, 8, 9, 10 and 12, the back pressure chamber at the back of the sliding vane 14 may be communicated with the second suction port 21, so as to implement a two-stage compression band intermediate cooling mode of the compressor 10, thereby increasing the working efficiency of the compressor 10.

In some embodiments of the present invention, as shown in fig. 3, the compressor 10 may further include: the three-way valve here is the first three-way valve 6, the first interface 61 of the first three-way valve 6 may be communicated with the back pressure cavity at the back of the sliding vane 14, the second interface 62 of the first three-way valve 6 may be communicated with the exhaust pipe 64 on the casing of the compressor 10, the third interface 63 of the first three-way valve 6 may be communicated with the reservoir 5 of the compressor 10, and the first interface 61 of the first three-way valve 6 may be selectively communicated with the second interface 62 and the third interface 63, so that the back pressure cavity may be communicated with the exhaust pipe 64 on the casing, and the back pressure cavity may be communicated with the reservoir 5. The arrangement enables the back pressure cavity to be communicated with high pressure or low pressure, the pressure of the back pressure cavity is controlled through the first three-way valve 6, whether the sliding piece 14 is separated from the back pressure cavity or not can be controlled, and therefore the variable capacity operation of the compressor 10 can be controlled.

In some embodiments of the present invention, as shown in fig. 4, the accumulator 5 of the compressor 10 is connected to the first suction port 11 and the second suction port 21, respectively, the first opening and closing valve 7 is provided between the second suction port 21 and the accumulator 5, and the first discharge port 12 and the back pressure chamber in the back of the vane 14 are connected to the second suction port 21 without passing through the first opening and closing valve 7. Wherein, set up like this and can guarantee the back pressure chamber of first cylinder 1 and the second induction port 21 intercommunication of second cylinder 2 to can guarantee that the second induction port 21 pressure of second cylinder 2 can appear high low pressure and switch, and then can reach the work purpose that corresponds the variable capacity operation of controlling first cylinder 1, and, so set up and to have saved a three-way valve, simple structure can reduce manufacturing cost.

In some embodiments of the present invention, as shown in fig. 13, the compressor 10 may further include: the three-way valve here is a three-way valve in which a first port 91 of the second three-way valve 9 is connected to the first exhaust port 12, a second port 92 of the second three-way valve 9 is connected to the second suction port 21, a third port 93 of the second three-way valve 9 is connected to the first suction port 11, the accumulator 5 of the compressor 10 is connected to the first suction port 11, and the second port 92 can be selectively communicated with one of the first port 91 and the third port 93. When the first port 91 is communicated with the second port 92, the refrigerant discharged from the first exhaust port 12 may flow into the second cylinder 2, so as to achieve the working purpose of the compressor 10 in variable capacity operation.

As shown in fig. 2-13, a refrigeration system 20 according to an embodiment of the present invention is characterized by including the above-mentioned compressor 10, the compressor 10 is installed on the refrigeration system 20, the compressor 10 can control the refrigeration system 20 to operate in a single-stage compression mode or a two-stage compression band intercooling mode, and V2 and V1 satisfy the relation: V2/V1 is more than or equal to 40% and less than or equal to 70%, so that the refrigeration system 20 can be ensured to have optimal energy efficiency, and the seasonal energy efficiency of the refrigeration system 20 can be improved.

In some embodiments of the present invention, as shown in fig. 2 to 13, the refrigeration system 20 may include an outdoor heat exchanger 201, an indoor heat exchanger 202, and an injection device 203, the injection device 203 is connected between the indoor heat exchanger 202 and the outdoor heat exchanger 201, the injection device 203 may include an injection port 204, and the injection port 204 is configured to mix a low-temperature refrigerant injected from the injection device 204 with a high-temperature refrigerant discharged from the first exhaust port 12, so that the refrigerant discharged from the first exhaust port 11 is cooled, and the refrigerant is cooled and then enters the refrigerant of the second suction port 21. Here, the gas sucked into the second intake port 21 of the second cylinder 2 is supplied from the injection device 203 in addition to the exhaust gas from the first cylinder 1, and in this case, the gas is referred to as a two-stage compression band gas injection function, and similarly, the injection device 203 may inject the gas into the compressor 10, which is referred to as a two-stage compression band gas injection function. If the spraying device 203 sprays the liquid into the compressor 10, it is necessary to ensure that the sprayed liquid is mixed with the gas discharged from the superheated first exhaust port 12 and no liquid fluid is carried.

Moreover, since the temperature of the gas or liquid injected by the injection device 203 is lower than the temperature of the gas discharged from the first exhaust port 12, the temperature of the gas discharged from the first exhaust port 12 can be reduced after the gas or liquid injected by the injection device 203 is mixed with the gas discharged from the first exhaust port 12, that is, the gas discharged from the first exhaust port 12 has a cooling function, especially, the liquid injected by the injection device 203 can absorb huge heat after the phase change of the liquid, and the cooling effect of the gas discharged from the first exhaust port 12 is especially obvious. Meanwhile, it can be known from the pressure-enthalpy diagram analysis that the gas exhausted from the first exhaust port 12 is cooled to be beneficial to reducing the power consumption of the second cylinder 2, and the exhaust temperature of the second cylinder 2 can be reduced, so that the working performance of the refrigeration system 20 can be improved.

In some embodiments of the present invention, the injection device 203 may be configured as a gas-liquid separator or a first heat exchanger, as shown in fig. 2, fig. 3, fig. 4, fig. 7, fig. 8, fig. 9, fig. 10, fig. 11, fig. 12 and fig. 13, the injection device 203 is configured as a gas-liquid separator type, wherein after the liquid sprayed by the injection device 203 cools the gas discharged from the first exhaust port 12, the gas discharged from the first exhaust port 12 may be cooled into liquid, so that the second suction port 21 sucks the liquid, which may shorten the life of the compressor 10, and in order to prevent this, the liquid may be separated and removed through the gas-liquid separator, which may ensure that the second suction port 21 does not suck the liquid, and may prolong the life of the compressor 10. As shown in fig. 5 and 6, the injection device 203 is a first heat exchanger, and when the refrigerant flows through the first heat exchanger, the first heat exchanger can cool the refrigerant, so that the temperature of the gas injected into the second suction port 21 can be lowered, and the gas discharged from the first exhaust port 12 can be better cooled.

In some embodiments of the present invention, as shown in fig. 7, the refrigeration system 20 may further include: the second heat exchanger 205, the second heat exchanger 205 may be connected between the first exhaust port 12 and the second suction port 21, the second heat exchanger 205 may be configured to cool the refrigerant discharged through the first exhaust port 12 and entering the second suction port 21, the second heat exchanger 205 is configured to cool the superheated gas discharged from the first cylinder 1, and the suction temperature of the second suction port 21 may be prevented from being too high, so that the service life of the compressor 10 may be ensured.

In some embodiments of the present invention, as shown in fig. 8-10, an oil separator 206 may be disposed between the first exhaust port 12 and the injection device 203. Wherein, if the first exhaust port 12 is for not passing through between the casing inner space but directly discharging, its oil content can be very big, if the gaseous injection apparatus 203 of vapour and liquid separator type still passes through of first exhaust port 12 exhaust, and oil can only follow liquid fluid behind the vapour and liquid separator and flow to indoor heat exchanger 202 to can not get back to second cylinder 2 fast, cause indoor heat exchanger 202 to remain too much oil, thereby cause indoor heat exchanger 202 heat transfer to be obstructed, the performance descends, and cause compressor 10 to lack of oil easily. Therefore, in this case, it is preferable to add the oil separator 206 before the gas-liquid separator so that the oil amount is directly returned to the compressor 10 without going to the gas-liquid separator, and it is preferable that the oil passage outlet of the oil is communicated with the second cylinder 2 through the capillary tube, and the oil is returned to the first suction port 11, so that unnecessary high and low pressure leakage loss of the compressed fluid can be avoided, and the performance degradation of the compressor 10 can be prevented.

In some embodiments of the present invention, as shown in fig. 9 and 10, a third heat exchanger 8 may be provided between the oil separator 206 and the injection device 203, wherein the gas discharged from the first exhaust port 12 may be passed through the third heat exchanger 8, that is, the third heat exchanger 8 is used to cool the gas discharged from the first exhaust port 12, and the third heat exchanger 8 may be incorporated into the second heat exchanger 205, so that the heat exchange area of the second heat exchanger 205 may be increased.

In some embodiments of the present invention, as shown in fig. 8 to 10, a throttling device 207 may be provided between the oil separator 206 and the second suction port 21, and the amount of liquid spray may be adjusted by adjusting the opening degree of the throttling device 207, so that the amount of liquid spray may be within a reasonable range.

Here, the capacity of the compressor 10 refers to an actual suction volume of the compressor 10 in one compression cycle, and the cylinder capacity refers to an actual suction volume of a cylinder in one compression cycle. The capacities of the single-stage compression mode and the double-stage compression band intercooling mode are different, so that the load of the compressor 10 can be adjusted, the compressor 10 can be controlled to selectively operate in two capacity states of V1 and V2, and the seasonal energy efficiency of the system can be improved when the compressor is applied to a constant speed machine.

In the two-stage compression band cooling function, the optimum capacity ratio range of the second cylinder 2 to the first cylinder 1 is V2: when the capacity range of the compressor 10 is about 30% of the full capacity when the V1 is 30% -70%, the effect of improving the seasonal energy efficiency is the largest, that is, the capacity V2 which is optimal without considering other influencing factors is about 30% V1, however, because the motor efficiency of the constant speed compressor 10 is reduced along with the reduction of the load, the motor efficiency is reduced very seriously when the load reaches 30%, only considering the influence of the motor efficiency, the capacity ratio V2 is the best V1, and in summary, the optimal volume ratio exists, and experimental research shows that the seasonal energy efficiency of the refrigeration system 20 can be the best when the optimal capacity ratio is 40% -70%.

In some embodiments of the present invention, as shown in fig. 1, the compressor may have a two-step capacitor structure, that is: the fixed speed compressor 10 may have a two-stage capacitor structure. When the constant speed compressor 10 works, the motor of the constant speed compressor 10 needs to be matched with a capacitor to run, the optimal capacitance value needed by the motor is different when the actual full capacity runs and when the actual full capacity runs, and the capacitance value when the full capacity runs is larger than that when the partial capacity runs, if two-gear capacitors are adopted, the compressor 10 is matched with a large capacitor to run when the full capacity runs, and is matched with a small capacitor to run when the partial capacity runs, and compared with the capacitor which is also adopted when the partial capacity runs, the motor efficiency when the partial capacity runs is greatly improved.

In some embodiments of the present invention, as shown in fig. 1 and 2, fig. 2 is a schematic diagram of a refrigeration system 20, and fig. 1 is a wiring diagram of a compressor 10 with two capacitors. The compressor 10 is configured as a fixed speed compressor 10, and the fixed speed compressor 10 may include two cylinders, a first cylinder 1 having a capacity of V1, a second cylinder 2 having a capacity of V2, and a V2: v1 ═ 50%. The first cylinder 1 is a variable-capacity cylinder, a spring is cancelled at the back of the sliding sheet 14 of the first cylinder 1, and a back pressure cavity is arranged and communicated with the second air suction port 21 of the second cylinder 2. The four-way valve 4 can realize the following two connection modes: the first method comprises the following steps: the first port 41 communicates with the second port 42, the third port 43 communicates with the fourth port 44, and the second: the first port 41 communicates with the fourth port 44, and the second port 62 communicates with the third port 43.

When the four-way valve 4 is in the first connection form: the first air suction port 11 is communicated with the first exhaust port 12, the back pressure cavity of the first air cylinder 1 is communicated with the second air suction port 21 of the second air cylinder 2, and the second air suction port 21 is communicated with the outlet of the liquid storage device 5, so that the second air cylinder 2 sucks air from the liquid storage device 5 to be compressed and then is discharged in the connecting mode, the second air suction port 21 of the second air cylinder 2 is low pressure at the moment, the first air cylinder 1 is unloaded, the refrigerant is compressed once in the compressor 10 through the second air cylinder 2, namely, the compression mode is a single stage, and the working capacity of the compressor 10 is V2 in the mode.

When the four-way valve 4 is in the second connection form: the communication between the first air inlet 11 and the liquid storage device 5 is realized, the back pressure cavity of the first air cylinder 1 is communicated with the second air inlet 21 of the second air cylinder 2, the second air inlet 21 is communicated with the outlet of the first air outlet 12, in such a connection mode, the first cylinder 1 sucks air from the reservoir 5, compresses the air and then discharges the air, then the pressure reaches the second cylinder 2 to carry out the second compression, at this time, the pressure at the back of the sliding vane 14 of the first cylinder 1 is the exhaust pressure of the first cylinder 1 (the suction pressure of the second cylinder 2 is close to the exhaust pressure of the first cylinder 1), so the first cylinder 1 realizes the normal operation, the performance can be further improved by the refrigerant being compressed twice in the compressor 10, i.e. in the two-stage compression mode, and the first-stage discharge gas being cooled by the gas (or liquid) injected from the injection device 203 and then passing through the second cylinder 2, where the working capacity of the compressor 10 is V1.

Through above structure, realized the switching of double stage compression area intercooling mode with the single-stage compression mode, satisfied capacity ratio A through the design and become V2: v1 is 50%, so that in the above operation mode, better seasonal energy efficiency is ensured, which is embodied as follows:

in the two-stage compression band injection mode, the optimal capacity ratio range of the second cylinder 2 to the first cylinder 1 is about 50% to 100%, and the seasonal energy efficiency is optimal when the partial load capacity is about 40% to 70% of the full capacity, and in summary, the capacity ratio a may be considered as V2: when V1 is 50%, the energy efficiency level in the above two operation modes can be considered. In the two-stage compression-band intercooling mode, the preferred capacity ratio range of the second cylinder 2 to the first cylinder is about 30% to 70%, and when the partial load capacity is about 40% to 70% of the full capacity, the seasonal energy efficiency is best, and in summary, the capacity is designed to satisfy a condition that a is V2: when V1 is 50%, the energy efficiency level in the above two operation modes can be considered. The capacitance value of the optimal motor efficiency collocation calculated by the motor theory is as follows: the capacitance value of the capacitor is 60 muF when the capacitor is full, and 30 muF when the capacitor is partial.

As shown in fig. 1, it can be realized that no matter the full capacity or the partial capacity is realized, the motor can be operated with an optimal capacitance value, and the system energy efficiency is improved, where the first capacitance value is 30 μ F, the second capacitance value is 30 μ F, in the two-stage compression mode, the switch in fig. 1 is turned off, and the compressor 10 is operated with two parallel capacitors, that is, a superimposed value of the two capacitors is 60 μ F (30 μ F +30 μ F is 60 μ F), and when the partial capacity is operated, only the switch in fig. 1 needs to be turned off, so that only one capacitance value is effective when the partial capacity is operated, that is, only one effective capacitance value is required when the compressor 10 is operated, and the capacitance value is 30 μ F, so that the motor can be operated at a high efficiency when the partial capacity is operated.

In some embodiments of the present invention, as shown in fig. 9 and 10, fig. 9 is a dual stage compression band intercooling mode fluid flow diagram and fig. 10 is a single stage compression mode fluid flow diagram. The compressor 10 is a constant speed compressor 10, and includes two cylinders, the first cylinder 1 has a capacity of V1, the second cylinder 2 has a capacity of V2, and a is V2: v1 ═ 50%; the first cylinder 1 is a variable-capacity cylinder, a spring is cancelled at the back of the sliding vane 14 of the first cylinder 1, and a back pressure cavity is arranged and communicated with a second air suction port 21 of the second cylinder 2. The four-way valve 4 can realize the following two connection modes: the first method comprises the following steps: the first port 41 communicates with the second port 42, the third port 43 communicates with the fourth port 44, and the second: the first port 41 communicates with the fourth port 44, and the second port 62 communicates with the third port 43.

When the four-way valve 4 is in the first connection form: the communication between the first air suction port 11 and the first exhaust port 12 is realized, the back pressure cavity of the first air cylinder 1 is communicated with the second air suction port 21 of the second air cylinder 2, and the second air suction port 21 is communicated with the outlet of the liquid storage device 5, so that the second air cylinder 2 sucks air from the liquid storage device 5 to be compressed and then is discharged in the connection mode; since the second suction port 21 of the second cylinder 2 is at a low pressure at this time, the first cylinder 1 is unloaded, so that the refrigerant is compressed only once through the second cylinder 2 in the compressor 10, i.e., in the single-stage compression mode in which the operating capacity of the compressor 10 is V2.

When the four-way valve 4 is in the second connection form: the communication between the first air suction port 11 and the liquid storage device 5 is realized, the back pressure cavity of the first air cylinder 1 is communicated with the second air suction port 21 of the second air cylinder 2, the second air suction port 21 and the first exhaust port 12 are respectively communicated with two ends of the second heat exchanger 205, under the connection mode, the first air cylinder 1 sucks air from the liquid storage device 5, compresses the air and then reaches the second air cylinder 2 to be compressed for the second time after passing through the three heat exchangers and the injection device 203, at the moment, the back pressure of the sliding sheet 14 of the first air cylinder 1 is the exhaust pressure of the first air cylinder 1 (the suction pressure of the second air cylinder 2 is close to the exhaust pressure of the first air cylinder 1), so the normal operation of the first air cylinder 1 is realized, the refrigerant is compressed twice in the compressor 10, namely, the compression mode, and the air sucked by the second air cylinder 2 is supplemented, so the performance can be further, the first stage discharge is further cooled and performance is further improved, and the working capacity of the compressor 10 in this mode is V1.

After the fluid is cooled by the third heat exchanger 8, the fluid may have a liquid fluid, and after the liquid fluid is filtered by the spraying device 203, the cooled fluid flows to the second cylinder 2 to be compressed, so that the second cylinder 2 is prevented from sucking the liquid fluid. Fluid after first cylinder 1 compression is discharged from first exhaust port 12 back and is not filtered oil and just directly discharge compressor 10 through the casing inner space, consequently, has very high oil content, and the vapour and liquid separator has been passed through this moment, and oil flows along liquid fluid easily, make oil can not follow gaseous fluid and flow toward second induction port 21 and can't get back to compressor 10, but follow liquid fluid and flow toward indoor heat exchanger 202, thereby it is big to cause the interior oil content of indoor heat exchanger 202, hinder the heat transfer, still cause compressor 10 oil level to reduce or even lack of oil. In addition, in fig. 9 and 10, the oil return port communicates with the second suction port 21 after passing through the throttle device 207, and even if the refrigerant fluid leaks in the return flow path, no loss of capacity occurs. Through the scheme, the switching between the two-stage compression air injection mode and the single-stage compression mode is realized. The capacity ratio A is designed to be V2: v1 is 50%, so that in the above operation mode, better seasonal energy efficiency is ensured, which is embodied as follows:

in the two-stage compression-band intercooler mode, the optimal capacity ratio range of the second cylinder 2 to the first cylinder 1 is about 30% to 70%, and the seasonal energy efficiency is best when the partial load capacity is about 40% to 70% of the full capacity, and in summary, the capacity ratio a may be considered as V2: when V1 is 50%, the energy efficiency level in the above two operation modes can be considered. Similarly, the present embodiment also employs the circuit with the two-stage capacitor structure as shown in fig. 1, which is not specifically described herein.

In fig. 2, the back pressure chamber of the first cylinder 1 is schematically communicated with the second suction port 21, and the injection device 203 is a gas-liquid separator. The back pressure chamber of the first cylinder 1 in fig. 3 is communicated with the high and low pressures of the refrigeration system 20 through the first three-way valve 6. The embodiment shown in fig. 4 is a schematic view in which the four-way valve 4 in fig. 2 is replaced with a first opening and closing valve 7 in cooperation with another opening and closing valve. In fig. 5 the injection device 203 is arranged as a first heat exchanger and the exhaust gases of the first cylinder 1 do not pass this injection device 203. The exhaust gas of the first cylinder 1 in fig. 6 passes through the injection device 203. FIG. 7 is a comparison of FIG. 2: the refrigeration system 20 adds a second heat exchanger 205 and the exhaust gas of the first cylinder 1 passes through the second heat exchanger 205. FIG. 8 is compared with FIG. 2: the exhaust gas of the first cylinder 1 passes the injection means 203, an oil separator 206 is added and the separated oil is returned to the second cylinder 2 via a throttle 207. FIG. 9 is compared with FIG. 8: the refrigeration system 20 adds a third heat exchanger 8. Fig. 9 is a schematic diagram of compressor 10 operating in a dual stage compression band intercooling mode. Fig. 10 is a schematic diagram of compressor 10 operating a single stage compression mode. FIG. 11 is a comparison of FIG. 2: the refrigeration system 20 is added with a switching valve which consists of two four-way valves. In fig. 12, the four-way valve 4 is composed of a cut-off valve and a check valve. The four-way valve 4 in fig. 13 is composed of a three-way valve.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like 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 first cylinder having a first intake port and a first exhaust port, and a second cylinder having a second intake port and a second exhaust port, the first cylinder having a capacity of V1, the second cylinder having a capacity of V2;

the variable-capacity structure is arranged for controlling the first air cylinder to operate and work so as to compress or unload the refrigerant entering the first air cylinder;

the compressor has a single stage compression mode and a two-stage compression band intercooling mode,

the first cylinder is controlled to unload by the positive displacement structure and the second cylinder is operated when the compressor is in the single-stage compression mode,

when the compressor is in the two-stage compression band intermediate cooling mode, the first cylinder is controlled by the variable-volume structure to operate, the second cylinder also operates, the refrigerant sucked by the first air inlet is compressed by the first cylinder and then discharged from the first air outlet, the discharged refrigerant is cooled and then sucked by the second air inlet and compressed in the second cylinder, and the secondarily compressed refrigerant is discharged from the second air outlet, wherein the ratio relation between the V2 and the V1 is satisfied: V2/V1 is more than or equal to 40% and less than or equal to 70%.

2. The compressor of claim 1, wherein the first cylinder has a first vane slot and a vane slidable in the first vane slot, the vane being backed by a back pressure chamber, the back pressure chamber being selectively connected to a high pressure to operate the first cylinder or selectively connected to a low pressure to unload the first cylinder.

3. The compressor of claim 2, further comprising: a four-way valve having a first port connected to the first exhaust port, a second port connected to the first intake port, a third port connected to a reservoir of the compressor, and a fourth port connected to the second intake port, wherein the first port is communicated with the second port and the third port is communicated with the fourth port, or the first port is communicated with the fourth port and the second port is communicated with the third port.

4. The compressor of claim 2, wherein the back pressure chamber of the vane back communicates with the second suction port.

5. The compressor of claim 2, further comprising: the first interface of three-way valve with gleitbretter back the back pressure chamber intercommunication, the second interface of three-way valve with blast pipe intercommunication on the casing of compressor, the third interface of three-way valve with the reservoir intercommunication of compressor, the first interface of three-way valve can selectively communicate the second interface with the third interface.

6. The compressor of claim 2, wherein a reservoir of the compressor is connected to the first suction port and the second suction port, respectively, a first opening and closing valve is provided between the second suction port and the reservoir, and the first discharge port and the back pressure chamber of the vane back are connected to the second suction port without passing through the first opening and closing valve.

7. The compressor of claim 2, further comprising: the first interface of the three-way valve is connected with the first exhaust port, the second interface of the three-way valve is connected with the second air suction port, the third interface of the three-way valve is connected with the first air suction port, the liquid storage device of the compressor is connected with the first air suction port, and the second interface can be selectively communicated with one of the first interface and the third interface.

8. The compressor of claim 1, wherein the compressor is a fixed speed compressor.

9. The compressor of claim 8, wherein the compressor has a two-step capacitor structure.

10. A refrigeration system, characterized in that it comprises a compressor according to any one of claims 1-9.

11. The refrigeration system as claimed in claim 10, wherein the refrigeration system comprises an outdoor heat exchanger, an indoor heat exchanger, and an injection device connected between the indoor heat exchanger and the outdoor heat exchanger, the injection device has an injection port for mixing a low-temperature refrigerant injected from the injection port with a high-temperature refrigerant discharged from the first exhaust port, so that the refrigerant discharged from the first exhaust port is cooled, and the refrigerant enters the second suction port after being cooled.

12. The refrigeration system of claim 10, wherein the injection device is a gas-liquid separator or a first heat exchanger.

13. The refrigerant system as set forth in claim 11, further including: and the second heat exchanger is used for cooling the refrigerant which is discharged through the first exhaust port and enters the second suction port.

14. A refrigeration system as set forth in claim 11 wherein an oil separator is disposed between said first discharge port and said ejector, and a throttling device is disposed between said oil separator and said second suction port.