WO2015051537A1

WO2015051537A1 - Refrigeration circulation apparatus

Info

Publication number: WO2015051537A1
Application number: PCT/CN2013/085059
Authority: WO
Inventors: 小津政雄; 杨国用; 王玲
Original assignee: 广东美芝制冷设备有限公司
Priority date: 2013-10-11
Filing date: 2013-10-11
Publication date: 2015-04-16

Abstract

Provided is a refrigeration circulation apparatus comprising: a dual-cylinder rotary compressor; a liquid reservoir (107), wherein the liquid reservoir (107) is connected to a first compression cavity (11a) via a low-pressure air suction pipe (4); an indoor heat exchanger (100) and an outdoor heat exchanger (110); a gas-liquid separator (108), wherein the gas-liquid separator (108) is connected between the indoor heat exchanger (100) and the outdoor heat exchanger (110); and a medium-pressure air suction pipe (5), wherein the medium-pressure air suction pipe (5) is connected between a second compression cavity (11b) and the gas-liquid separator (108). The dual-cylinder rotary compressor comprises a housing (2) provided with an air discharge pipe (3), an electric machine (130) and a compression apparatus (140) arranged in the housing (2); wherein the compression apparatus (140) comprises a first cylinder (10a) provided with the first compression cavity (11a) and a first muffler (25a), and a second cylinder (10b) provided with the second compression cavity (11b) and a second muffler (25b). The first muffler (25a) and the second muffler (25b) are in communication with the air discharge pipe (3). The refrigeration circulation apparatus improves refrigerating capacity and also increases efficiency.

Description

Refrigeration cycle device

The present invention relates to a refrigeration cycle apparatus for a gas refrigerant jet type rotary compressor which is applied to an air conditioner, a refrigerator, or the like. Background technique

At present, the heating technology on the air conditioner, especially in the low outside air temperature, is improved, and even in principle, it has been a difficult problem for many years.

In order to solve this problem, in recent years, the application of the gas refrigerant injection method to the compressor and the refrigeration cycle has attracted attention, and in particular, research on the characteristics of the two-cylinder rotary compressor has progressed. However, I hope to improve the heating efficiency. In addition, the most popular household air conditioners for rotary compressors must consider cost increases. Therefore, the application and spread of the gas refrigerant jet type in a rotary compressor is limited. Summary of the invention

The present invention aims to solve at least one of the technical problems existing in the prior art. Accordingly, it is an object of the present invention to provide a refrigeration cycle apparatus which improves refrigeration capacity and improves efficiency.

A refrigerating cycle apparatus according to an embodiment of the present invention, comprising: a two-cylinder rotary compressor including a housing, a motor and a compression device disposed in the housing, the housing having a row a gas pipe, wherein the compression device includes a first cylinder having a first compression chamber and a first muffler, a second cylinder having a second compression chamber and a second muffler, and a first cylinder and a second An intermediate plate between the cylinders, wherein the first cylinder and the second cylinder have a compression angle of substantially 180 degrees, and the first muffler and the second muffler are in communication with the exhaust pipe; The accumulator is connected to the first compression chamber through a low pressure suction pipe; the indoor heat exchanger and the outdoor heat exchanger; the gas-liquid separator, the gas-liquid separator is connected to the indoor heat exchanger and the outdoor heat And an intermediate pressure suction pipe connected between the second compression chamber and the gas-liquid separator to supply gas separated by the gas-liquid separator In the second compression chamber.

Thereby, the first cylinder sucks in the low-pressure refrigerant that has passed through the evaporator, and the second cylinder sucks in the gas refrigerant generated in the gas-liquid separator. The high-pressure refrigerant discharged from the respective independent cylinders passes through the first muffler and the second muffler and then flows out from the exhaust pipe, thereby simplifying the structure and improving the refrigeration capacity and modification. Good efficiency. In addition, if necessary, the power consumption can be reduced by stopping the compression of the second cylinder. According to an embodiment of the present invention, the refrigeration cycle apparatus further includes: a four-way port, four ports of the four-way port and the exhaust pipe, the accumulator, the indoor heat exchanger, and The outdoor heat exchangers are connected.

According to an embodiment of the present invention, the refrigeration cycle apparatus further includes: a first expansion port disposed between the indoor heat exchanger and the gas-liquid separator for heat from the room a refrigerant decompressed by the exchanger; and a second expansion crucible disposed between the gas-liquid separator and the outdoor heat exchanger for reducing refrigerant discharged from the gas-liquid separator Pressure.

According to an embodiment of the present invention, the second muffler is in communication with the first muffler through a communication hole formed in the first cylinder and the second cylinder.

According to another embodiment of the present invention, the housing includes an upper cover, and an exhaust chamber communicating with the exhaust pipe is defined between the upper cover and a top of the motor, and the second muffler passes An L-shaped tube is in communication with the exhaust chamber, and the exhaust chamber is in communication with the first muffler.

According to an embodiment of the invention, the displacement of the second compression chamber of the second cylinder is 10% - 25% of the displacement of the first compression chamber of the first cylinder.

According to an embodiment of the invention, a rear end of the second vane groove provided in the second cylinder is provided with a magnet for magnetically engaging a second vane located in the second vane groove.

The refrigeration cycle apparatus further includes: a switching device configured to switch a pressure in the second compression chamber between Pd and Pi, wherein Pd is a refrigerant discharged from the exhaust pipe The pressure value, Pi, is the pressure value of the refrigerant discharged from the gas-liquid separator.

According to an embodiment of the present invention, the switching device includes: a first one-way crucible, the first one-way crucible is located on a refrigerant conveying pipe between the medium-pressure suction pipe and the gas-liquid separator; And a two-way crucible, one end of the bidirectional crucible being connected to the pipeline between the exhaust pipe and the four-way crucible, and the other end being connected to the first one-way crucible and the medium-pressure suction pipe Between the pipes.

According to another embodiment of the present invention, the switching device includes: a first one-way turn, the first one-way turn is located on a refrigerant transfer pipe between the medium-pressure intake pipe and the gas-liquid separator And a second one-way crucible, the inlet end of the second one-way crucible is connected to the conduit of the four-way crucible and the outdoor heat exchanger, and an outlet end thereof is connected to the first one-way crucible The pipeline between the medium pressure suction pipes.

According to an embodiment of the present invention, the two-cylinder rotary compressor is configured to start, and after the first compression chamber starts compression, the second compression chamber begins to compress.

The refrigeration cycle apparatus according to the embodiment of the present invention has a simple structure and can improve the heating capacity. Compared with the phase of the jet-type rotary rotary compression and compression machine with the usual gas-cooling medium, it is possible to reduce the loss of low expansion and expansion. . In addition, due to the comfort and adaptability of the air conditioning and air conditioning, it has the ability to stop the cold refrigerant injection into the vehicle or The function of canceling the function of stopping and stopping is stopped. . Moreover, the manufacturing performance is good and good, and the advantage is that it can be borrowed for use in the production of parts and products. .

The additional aspects and advantages of the present invention will be given in the middle portion of the lower surface, and the partial portion will be described from 55 below. It is obvious that the change in the description has become obvious, or it has been understood through the practice of the invention. . Attached to the drawings

The above-mentioned and/or or additional aspects and advantages of the invention will be apparent from the following description of the embodiments. Lieutenant General will become more obvious and easy to understand, and among them:

1100 FIG. 11 is a schematic view showing the arrangement of a cold-frozen circulation cycle device according to the first embodiment of the present invention, wherein the rotation is shown A cross-sectional view of a rotary compression and compression machine;

Figure 22 is a detailed detailed sectional view of the center-rotating rotary compression and compression machine of Figure 11;

Figure 33 is a PP__HH line diagram of the cold freezing cycle loop device shown in Figure 11;

Figure 44 is a detailed detailed sectional section of a medium-rotary rotary compression compression machine according to the second embodiment of the present invention.

1155 Figure;

Figure 55 is a schematic view showing the root of the cold-frozen circulation cycle device according to the second embodiment of the present invention, which is shown in Figure 44, , wherein the second and second pairs of the two-way two-way two-way closed to the closed, the first one pair of two-way two-way closed to open the closed;

Figure 66aa and Figure 66bb are side elevational cross-sectional views of the second two-cylinder cylinder in the cold-frozen circulation cycle device shown in Figure 55. And a top view of the cross-sectional view;

2200 FIG. 77 is a schematic view showing the root of the cold freezing cycle loop device according to the second embodiment of the present invention, which is shown in FIG. , wherein the second and second pairs of the two-way open to the beating open, the first one pair of two-way to the closed and closed;

Figures 88aa and 88bb are side cross-sectional views of the second two-cylinder cylinder in the cold-frozen cycle-cycling device shown in Figure 77 and a top view of a cross-sectional view;

Figure 99 is a schematic view showing the arrangement of a cold-frozen cycle-circulating device according to a third embodiment of the present invention, in which a swirl is shown

Sectional view of the 2255 rotary compression and compression machine;

Figure 1100 is a schematic view of a cold freezing cycle loop device according to the fourth embodiment of the present invention, wherein the rotation is shown A cross-sectional view of a rotary compression and compression machine. .

Figure 11 is a schematic view of a cold-frozen cycle loop device according to the fifth embodiment of the present invention, wherein the rotation is shown A sectional view of a rotary compression and compression machine. .

3300 attached with the icon mark::

44, low and low pressure suction suction air pipe; 55, medium and medium pressure suction suction pipe;

l la, the first compression chamber; l lb, the second compression chamber;

25a, the first muffler; 25b, the second muffler;

100, indoor heat exchanger;

102a, a first expansion enthalpy; 102b, a second expansion enthalpy;

103, a gas refrigerant delivery pipe;

105, four-way switch; 106a, first two-way switch; 106b, second two-way switch;

108, gas-liquid separator; 110, outdoor heat exchanger;

116, three-way 闽;

120, rotary compressor;

130, motor; 140, compression device

The embodiments of the present invention are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are intended to be illustrative of the invention and are not to be construed as limiting.

In the description of the present invention, it is to be understood that the terms "center", "vertical", "transverse", "upper", "lower", "previous", "rear", "left", "right", " The orientation or positional relationship of the indications "upright", "horizontal", "top", "bottom", "inside", "outside", etc. is based on the orientation or positional relationship shown in the drawings, only for the convenience of describing the present invention and The simplification of the description is not intended to limit or imply that the device or elements referred to have a particular orientation, construction and operation in a particular orientation. Moreover, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining "first" and "second" may include one or more of the features, either explicitly or implicitly. In the description of the present invention, "multiple" means two or more unless otherwise stated.

In the description of the present invention, it should be noted that the terms "installation", "connected", and "connected" should be understood broadly, and may be either fixed or detachable, unless explicitly stated or defined otherwise. Connected, or connected integrally; can be mechanical or electrical; can be directly connected, or indirectly connected through an intermediate medium, can be the internal communication of the two components. The specific meanings of the above terms in the present invention can be understood in the specific circumstances by those skilled in the art. A refrigeration cycle apparatus according to an embodiment of the present invention, which is a refrigerant circulation type circulation apparatus or a refrigerant circulation type reversible heat pump circulation apparatus, will be described below with reference to Figs.

A refrigeration cycle apparatus according to an embodiment of the present invention includes: a two-cylinder rotary compressor, a liquid storage device

107. The indoor heat exchanger 100 and the outdoor heat exchanger 110, the gas-liquid separator 108, the four-way port 105, and the intermediate-pressure suction pipe 5.

As shown in FIGS. 1 to 11, the two-cylinder rotary compressor includes a housing 2, a motor 130 disposed in the housing 2, and a compression device 140 having an exhaust pipe 3 thereon, wherein the compression device includes the first The compression chamber 11a and the first cylinder 10a of the first muffler 25a, the second cylinder 10b having the second compression chamber 1 ib and the second muffler 25b, and the intermediate between the first cylinder 10a and the second cylinder 10b The plate 17, the first cylinder 10a and the second cylinder 10b have a compression angle of substantially 180 degrees, and the first muffler 25a and the second muffler 25b communicate with the exhaust pipe 3.

The accumulator 107 is connected to the first compression chamber l la through a low pressure suction pipe 4. The gas-liquid separator 108 is connected between the indoor heat exchanger 100 and the outdoor heat exchanger 110, and the intermediate pressure suction pipe 5 is connected between the second compression chamber 1 ib and the gas-liquid separator 108 to separate the gas-liquid separator 108. The gas is supplied into the second compression chamber 1 ib. When the four-way port 105 is selectively installed (Fig. 1, Fig. 5, Fig. 7, Fig. 9 and Fig. 10), the four ports of the four port 105 are respectively associated with the exhaust pipe 3, the accumulator 107, and the indoor heat exchanger. 100 is coupled to the outdoor heat exchanger 110. The cooling and heating mode is converted by switching the four-way port 105. In the heating mode, the indoor heat exchanger 100 is configured as a condenser, and the outdoor heat exchanger 110 is configured as an evaporator. In the cooling mode, the indoor heat exchanger 100 is configured as an evaporator, and the outdoor heat exchanger 110 is configured as an evaporator. Constructed as a condenser. As shown in Fig. 11, when the four-way weir is not installed, the exhaust pipe 3 is connected to the outdoor heat exchanger 110, and the accumulator 107 is connected to the outdoor heat exchanger 100, at which time the indoor heat exchanger 100 is constructed as an evaporator. The outdoor heat exchanger 110 is constructed as a condenser.

Thereby, the first cylinder 10a sucks in the low-pressure refrigerant that has passed through the evaporator, and the second cylinder 10b sucks in the gas refrigerant generated in the gas-liquid separator 108. The high-pressure refrigerant discharged from the respective independent cylinders passes through the first muffler 25a and the second muffler 25b, respectively, and then flows out from the exhaust pipe 3, whereby the structure is simple, and the refrigeration ability and the efficiency are improved. Further, if necessary, the power consumption can be reduced by stopping the compression of the second cylinder 10b.

According to some embodiments of the present invention, as shown in FIG. 1, the refrigeration cycle apparatus further includes a first expansion port 102a and a second expansion port 102b, and the first expansion port 102a is disposed between the indoor heat exchanger 100 and the gas-liquid separator 108. For decompressing the refrigerant discharged from the indoor heat exchanger 100, the second expansion port 102b is provided between the gas-liquid separator 108 and the outdoor heat exchanger 110 for separating the gas and liquid. The refrigerant discharged from the unit 108 is decompressed.

According to an embodiment of the present invention, as shown in Fig. 2, the second muffler 25b and the first muffler 25a communicate with each other through the communication hole 27 formed in the first cylinder 10a and the second cylinder 10b. Thereby, the refrigerant that has flowed out of the second cylinder 10b to the second muffler 25b enters the first muffler 25a through the communication hole 27, merges with the refrigerant flowing out of the first cylinder 10a, and then flows out of the exhaust pipe 3.

According to another embodiment of the present invention, as shown in FIG. 10, the housing 2 includes an upper cover 6, and the upper cover 6 defines a discharge chamber 40 communicating with the exhaust pipe 3 between the top of the motor 130, and the second silencer The damper 25b communicates with the exhaust chamber 40 through the L-shaped tube 7, and the exhaust chamber 40 communicates with the first muffler 25a. Thereby, the refrigerant that has flowed out of the second cylinder 10b to the second muffler 25b is discharged into the exhaust chamber 40 through the L-shaped tube 7, and the refrigerant that has flowed out of the first cylinder 10a to the first muffler 25a from the inside of the motor 130 It flows out into the exhaust chamber 40 to merge with the refrigerant flowing out of the second muffler 25b, and then flows out of the exhaust pipe 3.

Preferably, the displacement of the second compression chamber l ib of the second cylinder 10b is 10% - 25% of the displacement of the first compression chamber 11a of the first cylinder 10a.

According to some embodiments of the present invention, the rear end of the second vane groove 17b provided in the second cylinder 10b is provided with a magnet 16 for magnetically engaging the second vane 12b located in the second vane groove 17b.

According to a further embodiment of the present invention, the refrigeration cycle apparatus further includes a switching device configured to switch the pressure in the second compression chamber 1 ib between Pd and Pi, wherein Pd is in the exhaust pipe 3 The pressure value of the discharged refrigerant, Pi, is the pressure value of the refrigerant discharged from the gas-liquid separator 108.

As shown in FIG. 5-8b, in a specific embodiment of the present invention, the switching device comprises: a first bidirectional raft 106a and a second bidirectional raft 106b, the first bidirectional raft 106a being located at the intermediate pressure suction pipe 5 and the gas-liquid separation On the refrigerant delivery pipe 103 between the vessels 108, one end of the second bidirectional weir 106b is connected to the pipeline between the exhaust pipe 3 and the four-way weir 105, and the other end is connected to the first one-way weir 116a and the middle pressurizing On the line between the trachea 5.

As shown in FIG. 9, in another embodiment of the present invention, the switching device includes a three-way port 116 connected between the intermediate pressure intake pipe 5, the refrigerant delivery pipe 103, and the exhaust pipe 3 and the four-way port 105. The line, and the three-way port 116 can switch the pressure in the second compression chamber 1 ib between Pd and Pi.

As shown in FIG. 11, in another embodiment of the present invention, the switching device includes a three-way device

116 is connected to the intermediate pressure suction pipe 5, the refrigerant delivery pipe 103 and the pipeline between the exhaust pipe 3 and the outdoor heat exchanger 110, respectively, and the three-way port 116 can press the pressure in the second compression chamber 1 ib in the Pd and Between Pi Switch.

Preferably, the two-cylinder rotary compressor is configured to start, and when the first compression chamber 11a starts compression, the second compression chamber l ib starts to compress.

The refrigeration cycle apparatus according to the embodiment of the present invention has a simple structure and can improve the heating capacity, and can reduce the expansion loss as compared with the conventional gas refrigerant injection type rotary compressor. In addition, due to the comfort and energy efficiency of the air conditioner, it has the function of stopping the injection or stopping the refrigerant. Moreover, it has good manufacturability, and has the advantage that it can borrow conventional parts and mass production equipment. A refrigeration cycle apparatus according to various embodiments of the present invention will be described in detail below with reference to Figs.

[Embodiment 1]

The twin-cylinder rotary compressor (120) shown in Fig. 1 is composed of a variable-speed motor unit 130 having a variable rotational speed in the sealed casing (2) and a compression element (140) disposed under the motor unit (130). The high-pressure gas refrigerant (pressure Pd) discharged from the exhaust pipe 3 passes through the four-way crucible 105, and becomes a condensed refrigerant in the indoor heat exchanger 100. Thereafter, the first expansion enthalpy 102a is used to depressurize the liquid refrigerant in the gas. The liquid separator 108 is separated into a medium pressure gas refrigerant (pressure Pi) and a liquid refrigerant. Therefore, the supercooling of the liquid refrigerant is increased.

The liquid refrigerant continues to be decompressed by the second expansion port 102b, becomes a low-pressure gas refrigerant (pressure PS) in the outdoor heat exchanger 110, and thereafter, after passing through the four-way port 105 and the accumulator 107, is connected to the first cylinder 10a. Flow into the low pressure suction pipe. In addition, the above two expansion enthalpies are electronic expansion enthalpy which can control the flow rate of the refrigerant. The solid line (1) in Figure 1 shows the flow direction of the high-pressure refrigerant and the medium-pressure gas refrigerant (Pi), and the dotted line (一一 > ) shows the flow direction of the low-pressure refrigerant (PS).

The compressed high-pressure gas refrigerant sucked from the low-pressure suction pipe 4 to the first compression chamber 11a (shown in Fig. 2) of the first cylinder 10a is discharged into the first muffler 25a. On the other hand, the separated gas refrigerant (pressure Pi) in the gas-liquid separator 108 is sucked from the intermediate pressure suction pipe 5 through the refrigerant delivery pipe 103 to the second compression chamber 1 ib of the second cylinder 10b (as shown in FIG. 2). )in. The compressed high pressure refrigerant in the second compression chamber l ib is discharged into the second muffler 25b. The high-pressure refrigerant of the second muffler 25b passes through the communication hole 27 and merges with the high-pressure refrigerant of the first muffler 25a. Therefore, the refrigerants of different temperatures are mixed to become the refrigerant of the same temperature.

Among them, those skilled in the art should understand the range of the pressure value Pd of the high-pressure gas refrigerant discharged from the two-cylinder rotary compressor, the range of the pressure value Pi of the medium-pressure gas refrigerant, and the pressure value Ps of the low-pressure gas refrigerant. range. The gas refrigerant pressure discharged from the second cylinder 10b is normally the same as the gas refrigerant pressure discharged from the first cylinder 10a, the pressure thereof and the internal pressure of the casing 2 and the high pressure of the exhaust pipe 3 ( Pd) is the same. Further, the gas refrigerant discharged from the first muffler 25a is discharged from the exhaust pipe 3 while cooling the motor 130. Thus, Figure 1 shows a heat pump cycle system for refrigerant circulation. In this case, the first embodiment of the present invention is characterized in that the first cylinder 10a and the second cylinder 10b are independent, and the suction refrigerant pressure is different from the low pressure gas (PS) and the medium pressure gas (Pi), but each compression chamber The exhaust gas pressures are the same and they merge at the silencer.

The details of the compression element 140 fixed to the inner diameter of the casing 2 are as shown in Fig. 2. The compression element 140 is a first cylinder 10a fixed to the inner diameter of the casing 2, a second cylinder 10b fixed by the first cylinder 10a via the intermediate plate 17, and a first compression chamber 11a and a second compression chamber provided at the center of each cylinder. Llb, the pistons 14a and 14b disposed therein, the slider 12a and the slider 12b (shown in FIG. 4) reciprocatingly sliding with the piston thereof, the crankshaft 30 driving the piston thereof, the main bearing 25 slidably supporting the crankshaft 30, and The sub-bearing 26 is formed. In addition, the compression angles of the above two cylinders are usually at a relative position of 180 degrees.

The main bearing 25 and the sub-bearing 26 are provided with exhaust means for the exhaust holes 24a and the exhaust holes 24b opened in the first compression chamber 11a and the second compression chamber lib. It is covered by the first muffler 25a and the second muffler 25b. Further, a refrigerating machine oil (hereinafter simply referred to as oil) for lubricating the compression element 140 is injected into the bottom of the casing 2, and is omitted in the drawings.

The ratio of the displacement of the first compression chamber 11a to the displacement of the second compression chamber lib can be obtained by the ratio of the amount of refrigerant in the circulation refrigeration cycle to the amount of injected refrigerant, and the compression ratio in each compression chamber Pd/PS t Pd/Pi (absolute Pressure) to set the approximate value. For example, when the motor speed is 60rPS, when Pd = 2.54, PS = 0.87, Pi = l.50 (MPa. abS), or g/G = 0.25, the displacement of the first compression chamber 11a is called Va, because The compression ratio, the displacement Vb of the second compression chamber lib is 0.58 times that of the first cylinder 10a, and considering g/G, Vb/Va = 0.145. For example, in the case of a household air conditioner, when the displacement Va of the first compression chamber 11a is 15 cc, when Vb/V _a = 0.2, the displacement Vb of the second cylinder 10b is 3.0 cc. In addition, due to the specifications and design conditions of the air conditioner, Vb/Va varies greatly, and a slight margin can be given. The lower limit of displacement Vb/Va should be 10%, and the upper limit should be 25%. As mentioned above, small displacement of The inner diameter and the height dimension of the second cylinder 10b are also reduced. Based on the publicity technique of Patent Document 1 (opening 1998-259787, rotary seal type compressor and refrigeration cycle device), the slide spring is omitted to prevent slippage due to machining. It is sensible to reduce the rigidity of the cylinder and the reduction of the sliding area of the sliding groove by the hole. Therefore, the embodiment described later is also a slide spring in which the second cylinder 10b is omitted. Further, if the vane spring is omitted, when the compressor is started, the compression is started from the first cylinder 10 having the vane spring, and the second cylinder 10b is also compressed after a few seconds.

The action of the small displacement second cylinder 10b can be explained by the fact that the refrigerant (Pi) whose pressure is lowered by the first expansion port 102a is compressed in the second compression chamber l ib to return to the pressure (Pd) of the casing 2. This design concept is different from the conventional gas refrigerant jet rotary compressor that injects a gas refrigerant into a compression chamber or a pressure passage.

For example, according to the method disclosed in Patent Document 2 (JP-A-2000-073974, 2-stage compressor and air conditioner) and Patent Document 1, the first stage compression chamber and the second stage are used in which two cylinders are used for two-stage compression. A gas refrigerant channel is designed between the segments of the compression. It is characterized by injecting a gas refrigerant having a higher pressure into the refrigerant passing through the intermediate pressure (Pm) of the gas refrigerant passage. Therefore, the two kinds of refrigerants of different pressures are mixed and flow into the second stage compression chamber. The high pressure refrigerant compressed again here is discharged to the inside of the casing. According to this method, the injection of a high-pressure gas refrigerant causes a loss of expansion. That is to say, since the expanded gas energy cannot be recovered, the compression efficiency is lowered. Moreover, the structure is more complicated, and additional piping and sealing silencers are required.

Fig. 3 is a P-h diagram of the first embodiment. Pd of the vertical axis is the discharge pressure of the first cylinder 10a and the second cylinder 10b, Pi is the injection pressure to the second cylinder 10b, and PS is the intake pressure of the first cylinder 10a. G is the refrigerant flow rate of the indoor heat exchanger 100, and g is the gas refrigerant injection flow rate. Therefore, the refrigerant flow rate of the outdoor heat exchanger 110 is G-g.

Since the present invention is characterized in that the first cylinder 10a and the second cylinder 10b are independent and compress gases of different pressures, the respective compression amounts (W) can be expressed by il (Gg) and i2 (g). Therefore, it can be confirmed again that the second cylinder 10b simply raises the gas refrigerant pressure Pi to the pressure Pd. In addition, even if the pressure Pi changes, the exhaust pressure Pd usually adapts to the housing pressure. Further, in order to increase or decrease the operating speed (rPS) of the variable speed motor 130, the refrigerant flow rate G and the heating capacity of the indoor heat exchanger 100 are increased or decreased according to its condition, but since the first cylinder 10a and the second cylinder The operating speed of the cylinder 10b is generally the same, so the value (ratio) of g/G does not vary much. Embodiment 1 is a reversible refrigeration cycle device having a four-way port 105 as long as the reverse rotation mode is used. Switch to the four-way port 105 of the cooling mode. At the same time, gas refrigerant injection is performed even in the cooling mode. Further, Embodiment 1 can be applied to a rocking type rotary compressor in which a piston and a slider are integrated. Further, Embodiment 1 can be applied to a swing type rotary compressor in which a piston and a slider are integrated. [Embodiment 2]

From the viewpoint of comfort and energy efficiency in one year of the air conditioner, there is a product plan in which neither the heating mode nor the cooling mode uses the gas refrigerant injection, or there is a product in which the gas refrigerant injection is suspended during the operation by the selection mode. Planning. Further, it is necessary to stop the gas refrigerant injection in a state in which the air conditioning load is small in the middle of the night and the dehumidification operation or the low-load operation after the room temperature is stabilized. As a means for achieving the object, the second embodiment relates to a technique of stopping or releasing the compression of the second cylinder 10b having a small displacement.

First, the design change point of the second embodiment will be described as compared with the first embodiment. 4 is a cross-sectional view of the compression element 140, and in the second embodiment, a magnet 16 is provided at the rear end of the second vane groove 17b in which the slider 12b is placed. Thus, the magnetic force of the magnet 16 has a function of holding the slider 12b which has been stationary. So the magnetic force is small. Further, as shown in Fig. 5, the first bidirectional crucible 106a and the second bidirectional crucible 106b are added, and the first bidirectional crucible 106a is connected to the gas refrigerant delivery pipe 103. The second bidirectional raft 106b is connected to a high pressure circuit connecting the exhaust pipe 3 and the four-way port 105, and a circuit between the first one-way raft 106a and the intermediate-pressure suction pipe 5 on the gas refrigerant pipe 103.

Figure 5 shows the heating mode. When the second bidirectional 闽 106b is closed and the first bidirectional 闽 106a is simultaneously opened, the gas refrigerant (pressure Pi) of the gas-liquid separator 108 flows into the intermediate pressure intake pipe 5 to form a gas refrigerant injection. The action of the piston 14b and the slider 12b at this time is as shown in Figs. 6a and 6b. However, as shown in Fig. 7, if the second bidirectional 闽 106b is opened while the first bidirectional 闽 106a is closed, at this time, as shown in Figs. 8a and 8b, the pressure of the first compression chamber 1 ib is switched to The high pressure (Pd), since the slider 12b is attracted and held by the magnet 16 at the top dead center, the piston 14b in the second compression chamber 1 ib is idling and stops the compression. Therefore, the workload of the second cylinder 10b is zero, and the power consumption (W) of the compressor is lowered.

Next, as shown in Fig. 5, if the two-way crucible 106 is closed, since the first one-way crucible 116a is closed, the pressure of the intermediate-pressure suction pipe 5 is switched to the intermediate pressure (Pi). At the same time, since the pressure of the first compression chamber 1 ib is also switched from the high pressure to the intermediate pressure, since the back of the slider 12b is affected by the pressure difference (Pd - Pi ), the slider 12b is separated from the magnet 16. At the same time, gas refrigerant injection is started. Therefore, with the switching of the two-way weir 106, the pressure of the second compression chamber 1 ib is switched between Pd and Pi, and switching is temporarily performed between stopping the compression and releasing the stop. The two-way 闽 106 is independent of the switching of the four-way 闽 105, and generally functions as a high voltage, so the above principle is also true in the cooling mode. Therefore, in the second embodiment, the switch of the two-way port 106 can be used, and the gas refrigerant injection and the release stop can be freely stopped regardless of the operation mode and the operation load, and can be applied to the comfort of the air conditioner and the improvement of the annual efficiency (APF). .

[Embodiment 3]

The embodiment 3 shown in Fig. 9 is an application of the embodiment 2, and can be used when stopping the gas refrigerant injection regardless of the heating mode or the cooling mode state. Here, the gas refrigerant injection is turned on in the heating mode, and is suspended in the cooling mode. Embodiment 3 A rotary compressor 120 is used in the same manner as in the second embodiment. The two-way 闽 106 is omitted, and the second one-way 闽 116b is added.

As shown in FIG. 9, the three-way port 116 is connected to the intermediate pressure suction pipe 5, the refrigerant delivery pipe 103, and the pipeline between the exhaust pipe 3 and the four-way port 105, and can be selectively passed through the three-way port 116. The pressure suction pipe 5 is in communication with the refrigerant delivery pipe 103, and at this time, one end of the pipe connecting the three-way port 116 to the exhaust pipe 3 and the four-way port 105 is closed. Further, the gas refrigerant (pressure Pi) of the gas-liquid separator 108 flows into the intermediate pressure intake pipe 5 to form a gas refrigerant injection. Alternatively, the medium pressure suction pipe 5 can be selectively connected to the pipeline between the exhaust pipe 3 and the four-way port 105 through the three-way port 116, and the end of the three-way port 116 connected to the refrigerant pipe 103 is closed. of. Further, the pressure of the first compression chamber l ib is switched to the high pressure (Pd ), and in turn, the principle of the second embodiment, the piston 14b in the second compression chamber l ib stops the idling stop.

[Embodiment 4]

When the operating conditions are drastically changed, the gas refrigerant generated in the gas-liquid separator 108 is less, and after passing through the gas refrigerant delivery pipe 103, the gas-liquid mixed refrigerant or liquid refrigerant is sent to the second compression chamber l ib . If this state is continued, the temperature of the discharge refrigerant of the second cylinder 10b is drastically lowered, and the temperature of the oil 6 stored at the bottom of the casing 2 is seriously lowered.

If the difference between the oil temperature (To) and the condenser's saturated condensation temperature (TC) is called oil superheat (BSH), it is desirable that BSH = To_Tc > 5 °C. As a case, if BSH < 0 °C, the oil 6 in the casing is dissolved by more than 40% of the refrigerant, and the viscosity of the oil 6 is greatly reduced after being diluted. Problems such as crankshaft wear and tear often occur due to a significant drop in viscosity.

The fourth embodiment shown in Fig. 10 is a means for solving the above problems. The low-temperature refrigerant discharged from the second cylinder 10b to the second muffler 25b passes through the L-shaped tube 7 and flows into the exhaust chamber 40 surrounded by the upper portion of the motor 130 and the upper cover 6. On the other hand, the low-pressure refrigerant passing through the evaporator is discharged from the first cylinder 10a to the first muffler 25a, and then flows into the exhaust chamber 40 through the inside of the motor 130. Therefore, with the L-shaped tube 7 After the low-temperature refrigerant is mixed, it is discharged from the exhaust pipe 3 to the refrigeration cycle apparatus.

As a result, the low-temperature refrigerant discharged from the second cylinder 10b is not in contact with the oil 6 stored at the bottom of the casing, and is discharged from the exhaust pipe 3. In other words, the oil superheating (BSH) can be prevented by the injection of gas-liquid mixed refrigerant or liquid refrigerant. Further, in Fig. 10, the front end of the L-shaped tube 7 is connected to the core slit groove 8 provided on the outer diameter of the motor core.

[Embodiment 5]

Figure 11 shows a case of Embodiment 5, Embodiment 5 is another application based on Embodiment 3, Embodiment 5 eliminates the four-way port of Embodiment 3, and Embodiment 5 is an irreversible refrigeration cycle device In the case of simple cooling or heating, in the fifth embodiment, the three-way port 116 is connected to the intermediate pressure suction pipe 5, the refrigerant conveying pipe 103, and the pipeline between the exhaust pipe 3 and the outdoor heat exchanger 110, respectively. And the three-way port 116 can switch the pressure in the second compression chamber 1 ib between Pd and Pi. The working principle is the same as that of the third embodiment, and those skilled in the art can understand according to the description of the third embodiment, and details are not described herein again. The refrigeration cycle apparatus according to an embodiment of the present invention has the following advantages:

(1) Since the first and second cylinders are independent of each other, the refrigerant having different pressures is sucked in and compressed. The first cylinder 10a sucks the low-pressure gas that has been evaporated, the second cylinder 10b sucks the intermediate-pressure gas (Pi) of the gas-liquid separator 108, and discharges the high-pressure gas equivalent to the pressure (Pd) of the casing 2, respectively, at the muffler 25a. confluence. As a result, the compression efficiency can be improved by the optimized displacement, and the loss due to the re-expansion of the medium-pressure gas can be prevented.

(2) It is possible to freely stop the gas refrigerant injection and release, and improve the comfort and annual efficiency of the air conditioner.

(3) Since it is not a secondary compression method, it is not necessary to add a sealed silencer and an intermediate circuit. That is to say, it is possible to provide a compressor with a better cost and manufacturability as well as a simple refrigeration cycle device.

Embodiments 1 and 4 of the present invention can be applied to a swing type rotary compressor. Further, the rotary compressor can be applied not only to air conditioners but also to applications such as refrigeration equipment. In addition, the present invention can borrow parts and manufacturing equipment of the current two-cylinder rotary compressor.

Other configurations of the refrigeration cycle apparatus according to embodiments of the present invention, such as the crankshaft, piston, etc. of the rotary compressor, and operations are known to those skilled in the art and will not be described in detail herein.

In the description of the present specification, the description of the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples", etc. example The specific features, structures, materials, or characteristics described in the examples are included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms does not necessarily mean the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.

While the embodiments of the present invention have been shown and described, the embodiments of the invention may The scope of the invention is defined by the claims and their equivalents.

Claims

Claim

A refrigeration cycle device, comprising:

a two-cylinder rotary compressor comprising a housing (2), a motor (130) disposed within the housing, and a compression device (140) having an exhaust pipe (3) The compression device includes a first cylinder (10a) having a first compression chamber (11a) and a first silencer (25a), a second having a second compression chamber (lib) and a second silencer (25b) a cylinder (10b), and an intermediate plate (17) disposed between the first cylinder and the second cylinder, wherein a compression angle of the first cylinder and the second cylinder is substantially 180 degrees, the first silencer And the second muffler is in communication with the exhaust pipe;

a reservoir (107), the reservoir is connected to the first compression chamber through a low pressure suction pipe (4); an indoor heat exchanger (100) and an outdoor heat exchanger (110);

a gas-liquid separator (108) connected between the indoor heat exchanger and the outdoor heat exchanger;

a medium pressure suction pipe (5) connected between the second compression chamber (lib) and the gas-liquid separator (108) to separate the gas-liquid separator Gas is supplied into the second compression chamber (lib).

2. The refrigeration cycle apparatus according to claim 1, further comprising: a four-way port (105), wherein the four ports of the four-way port are respectively associated with the exhaust pipe, the accumulator, The indoor heat exchanger is connected to the outdoor heat exchanger.

The refrigerating cycle apparatus according to claim 1 or 2, further comprising: a first expansion weir (102a), the first expansion weir disposed in the indoor heat exchanger (100) and the Between gas-liquid separators (108); and

A second expansion port (102b) is disposed between the gas-liquid separator (108) and the outdoor heat exchanger (110).

The refrigeration cycle apparatus according to claim 1 or 2, wherein the second muffler and the first muffler pass through a communication hole formed in the first cylinder and the second cylinder

(27) Connected.

The refrigeration cycle apparatus according to claim 1 or 2, wherein the casing comprises an upper cover (6), and the upper cover (6) and the top of the motor are defined and An exhaust chamber (40) communicating with the exhaust pipe (3), the second muffler (25b) is in communication with the exhaust chamber (40) through an L-shaped tube (7), and the exhaust chamber (40) ) connected to the first silencer (25a) Pass.

The refrigeration cycle apparatus according to claim 1 or 2, wherein a displacement of the second compression chamber of the second cylinder is a displacement of the first compression chamber of the first cylinder 10% - 25%.

The refrigerating cycle apparatus according to claim 1 or 2, wherein a magnet (16) is disposed at a rear end of the second vane groove provided in the second cylinder, and the magnetic coupling is located at the a second sliding piece (12b) in the second sliding groove.

8. The refrigeration cycle apparatus according to claim 7, wherein: the switching device is configured to switch a pressure in the second compression chamber between Pd and Pi, Wherein Pd is a pressure value of the refrigerant discharged from the exhaust pipe, and Pi is a pressure value of the refrigerant discharged from the gas-liquid separator.

9. The refrigeration cycle apparatus according to claim 8, wherein the switching device comprises:

a first bidirectional crucible (106a), the first bidirectional crucible being located on the refrigerant delivery pipe (103) between the intermediate pressure intake pipe (5) and the gas-liquid separator (108);

a second bidirectional weir (106b), one end of the second bidirectional weir is connected to a pipeline between the exhaust pipe (3) and the four pass weir (105), and the other end is connected to the first On the line between the two-way weir (106a) and the medium-pressure suction pipe (5).

The switching device realizes pressure switching of the medium-pressure intake pipe (5) by controlling a switching state of the first bidirectional 闽 (106a) and the second bidirectional 闽 (106b), the first bidirectional 闽 (106a) And the second two-way 闽 (106b) cannot be turned on at the same time.

10. The refrigeration cycle apparatus according to claim 8, wherein the switching device comprises:

a three-way port (116), the three-way port is respectively connected to the medium-pressure suction pipe (5), the refrigerant conveying pipe (103), and the exhaust pipe (3), and then the intermediate pipe can be selectively The pressure of the pressure suction pipe (5) is switched to the pressure of the exhaust pipe (3) or the pressure of the refrigerant delivery pipe (103).

The refrigeration cycle apparatus according to claim 8, wherein the two-cylinder rotary compressor is configured to be activated, and after the first compression chamber is started to be compressed, the second compression chamber starts to be compressed.