WO2015117281A1

WO2015117281A1 - Volume control-type rotary compressor and refrigeration circulation apparatus having same

Info

Publication number: WO2015117281A1
Application number: PCT/CN2014/071934
Authority: WO
Inventors: 小津政雄; 梁双建; 王玲
Original assignee: 广东美芝制冷设备有限公司
Priority date: 2014-02-10
Filing date: 2014-02-10
Publication date: 2015-08-13

Abstract

A volume control-type rotary compressor and a refrigeration circulation apparatus having same. A compressing mechanism (5) of the volume control-type rotary compressor comprises: a first cylinder (10a) and a second cylinder (10b) that are each provided with a first compression cavity (13a) and with a second compression cavity (13b), and a partition plate (40) arranged between the first cylinder (10a) and the second cylinder (10b), where the partition plate (40) is in communication with an intake pipe (41), the thickness of the partition plate (40) is Hm, the thickness of the first cylinder (10a) is Ha, and the thickness of the second cylinder (10b) is Hb, satisfying the following relation: Hm³ > Ha³ + Hb³.

Description

Capacity control type rotary compressor and refrigeration cycle device therewith

Technical field

The present invention relates to the field of refrigeration, and more particularly to a capacity control type rotary compressor and a refrigeration cycle apparatus therewith. Background technique

In the two-cylinder capacity-controlled rotary compressor, the s mode deteriorates by several percentage points compared to the P mode. The main reasons are as follows: In the s mode, (1) Since the intake pipes connecting the cylinders are independent, the cylinders in operation do not suck in the intake of the stopped cylinders. (2) In order to improve the compression efficiency, the cylinder thickness is limited, so the suction passage cannot be enlarged and the suction efficiency can be improved. (3) Even if the cooling capacity is halved, the sliding loss will not be halved due to the rotation of the piston and the eccentric shaft. Summary of the invention

The present invention aims to solve at least one of the technical problems in the related art to some extent.

Accordingly, it is an object of the present invention to provide a capacity control type rotary compressor which improves compressor efficiency. Another object of the present invention is to provide a refrigeration cycle apparatus having the above-described capacity control type rotary compressor.

A capacity control type rotary compressor according to an embodiment of the present invention includes: a sealed casing; an electric motor, the electric motor is disposed in the sealed casing; a rotary compression mechanism, the rotary compression a mechanism is disposed in the sealed housing and coupled to the electric motor, the rotary compression mechanism comprising: a first cylinder and a second cylinder each having a first compression chamber and a second compression chamber; a middle partition between the first cylinder and the second cylinder, and the middle partition has an intake hole opening to the first compression chamber and the second compression chamber; a first piston and a second piston that respectively revolve in a compression chamber and the second compression chamber; a first sliding piece that can reciprocate with the respective revolutions of the first piston and the second piston a second sliding vane, and the second cylinder has a second vane cavity in which the back of the second vane is accommodated; the pressure of the sealed second vane chamber is between two different pressures Switching to stop or solve the compression of the second cylinder Stopping the pressure switch, wherein the separator is connected to the intake pipe; the thickness Hm of the separator is, the thickness Ha of the first cylinder is, the thickness of the second cylinder is Hb satisfies the following relationship: Hm ³ > Ha ³ + Hb ³ . According to the capacity control type rotary compressor of the embodiment of the present invention, in the S mode in which the second compression chamber is deactivated, the low pressure gas sucked from the intake pipe flows only into the first compression chamber, thereby improving the number The suction efficiency of a compression chamber improves compressor efficiency. Further, the capacity control type rotary compressor according to the above embodiment of the present invention may further have the following additional technical features:

In some examples of the invention, the thickness of the first cylinder is equal to the thickness of the second cylinder.

According to some embodiments of the invention, the pressure switch is in communication with the second vane cavity through the intermediate partition. According to some embodiments of the invention, the open portion of the second vane cavity is coupled to the deformable sealing plate to retain the second vane in the second vane cavity.

Specifically, the sealing plate has a deflection of 12 μm or more.

Specifically, the pressure switcher is a three-way valve or a four-way valve.

A refrigeration cycle apparatus according to an embodiment of the present invention includes a capacity control type rotary compressor according to the above embodiment of the present invention. DRAWINGS

Fig. 1 is a view showing the internal structure of a two-cylinder capacity-controlled rotary compressor and the configuration of a refrigeration cycle apparatus for connecting the compressor, and the operation principle of the three-way valve required for switching the operation mode;

Figure 2 shows a detailed longitudinal section of the compression mechanism (P-template); the middle partition is the F-X-G cross-sectional view of Figure 3, and the cylinder is the E-X-G cross-sectional view of Figure 3;

Fig. 3 is a view showing the configuration of the cylinder and the arrangement of the piston vanes, and the plan view (P mode) of the intake pipe and the pressure switching pipe connecting the intermediate partitions, and the Y cross section of Fig. 1;

Figure 4 is a longitudinal sectional view (P mode) showing the pressure switching tube and the slider chamber of the separator in the connection, which is a sectional view of E-X-G of Figure 3;

Figure 5 is a plan view (S mode) of the slider which is released from the rotating piston and is stationary in the vane cavity, and is a Y section of Fig. 1;

Fig. 6 is a plan view (S mode) of the slider which is stationary due to deformation of the sealing plate, and is a Z section of Fig. 1; Fig. 7 is a detailed longitudinal sectional view of the compression mechanism corresponding to Fig. 2 (P mode) ( S mode), the middle partition is the F-X-G sectional view of Fig. 6, and the cylinder is the E-X-G sectional view of Fig. 6;

Figure 8 is a comparison of the refrigeration capacity data of the conventional compressor and the present invention;

Fig. 9 is a comparison of the conventional compressor and the C 0 P data of the present invention. detailed description

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. A capacity-controlled rotary compressor in which one of the two cylinder compression chambers is operated in a non-compressed manner and the compressor capacity is switched in two stages, as shown in [Patent Document 1], the suction chamber is inhaled. The "compression chamber pressure switching method" method in which the pressure is switched between high pressure and low pressure, and as shown in [Patent Document 2] and [Patent Document 3], the pressure of the sealed vane chamber is made between high pressure and low pressure. The method of switching the "sliding chamber pressure switching method". They are characterized in that the reciprocating motion of the slider is stopped in a short time and housed in the slider cavity.

Two-cylinder capacity-controlled rotary compressor with two compression chambers for compression operation mode (P mode), one compression chamber for compression operation, and the other compression chamber for compression The operating mode (S mode) of the operation controls the cooling capacity of the compressor through the two different operating modes. As a result, for example, the air conditioner cooling capacity and power consumption can be controlled.

The above-mentioned "compression chamber pressure switching method", one of the intake pipe (low-pressure circuit) connected to the two cylinders, and one of the three-way valve (or four-way valve) and the compression chamber The pressure switches between high pressure and low pressure. By this control, the compression of one of the compression chambers can be stopped or stopped. Therefore, the "compression chamber pressure switching type" requires separate suction pipes in each cylinder.

In response to this, the "sliding chamber pressure switching method" can seal the sliding chamber of one cylinder, the internal pressure is switched between high pressure and low pressure, and the compression of the compression chamber is stopped (S mode), or released. Cylinder stop (P mode). Therefore, in the "pressure switching method of the vane chamber", it is not necessary to connect independent suction ducts of the two cylinders. The present invention focuses on the essence of the "sliding chamber pressure switching mode", which is characterized in that the suction pipe is not connected to the cylinder, and there is one suction passage, and the respective compression chambers are connected to the intermediate partition. Moreover, the operational efficiency of the S mode with a high frequency of operation is the main purpose.

In addition, in order to maintain the stopped slider, the "compression chamber pressure switching method" uses a magnet [Patent Document 1], and the "slide chamber pressure switching method" applies high and low pressure difference on both sides of the slider. (Patent Document 2 and Patent Document 3) According to the capacity control type rotary compressor of the embodiment of the present invention, the low pressure outlet pipe 72 of the accumulator 70 passes through the suction pipe 4 1 from the suction hole of the intermediate plate 40. The apex of the apex is provided with a slanting hole 4 3 a and a slanting hole 4 3 b communicating with the compression chamber 1 3 a and the compression chamber 1 3 b. In the P mode in which both compression chambers are compressed, the low pressure gas flowing out of the intake pipe 4 1 can be equally split into the above two compression chambers. The compression chamber 1 3 b is in the S mode operation in which the compression is stopped, and all of the low pressure gas flows only into the compression chamber 1 3 a, so the suction efficiency of the compression chamber 1 3 a is increased.

Regarding the annual operating rate and the general S mode, which is approximately three times that of the P mode, the efficiency improvement of the S mode can greatly contribute to improving the annual energy efficiency (A P F ). Moreover, the present invention has the effect of improving the efficiency of the P mode. In addition, by connecting an intake pipe to the intermediate partition, the two suction pipes can be reduced to one. In addition, the connection design of the pressure switching tube and the slider chamber can be improved as will be described later.

Among them, [Patent Document 1] JP 2 QQ 4 3 Q 1 1 1 4 Rotary sealed compressor and refrigeration cycle device [Patent Document 2] JP JP 2 0 0 8 5 2 0 9 0 1 Variable Capacity Rotary Compressor and Cooling System

[Patent Document 3] JP 2 QQ 8 1 2 8 2 3 1 Variable Capacity Rotary Compressor Specifically, a capacity control type rotary compressor 80 according to an embodiment of the present invention includes a sealed casing 1. The electric motor 6 and the rotary compression mechanism 5 are provided in the sealed casing 1. The rotary compression mechanism 5 is provided in the sealed casing 1 and is connected to the electric motor 6. Wherein, the compression mechanism 5 comprises: a first cylinder 10a and a second cylinder 10b each having a first compression chamber 13*1 and a second compression chamber 13b, disposed between the first cylinder 10a and the second cylinder 10b The intermediate partition 40 has an intake hole 45 in the intermediate partition 40 that opens to the first compression chamber 13a and the second compression chamber 13b, and is respectively performed in the first compression chamber 13a and the second compression chamber 13b. The revolving first piston 24a and the second piston 24b, with the respective revolutions of the first piston 24a and the second piston 24b, can reciprocate the first sliding piece 20a and the second sliding piece 20b, and the second cylinder The second vane chamber 15b having the back of the second vane 20b is accommodated in 10b, and the pressure of the sealed second vane chamber 15b is switched between two different pressures to compress the second cylinder 10b. The pressure switcher that performs the stop or the stop is stopped, wherein the middle partition 40 is connected to the intake pipe 41. Optionally, the pressure switch is a three-way valve 50 or a four-way valve.

Wherein, the thickness of the intermediate partition 40 is Hm, the thickness of the first cylinder 10a is Ha, and the thickness of the second cylinder 10b is Hb satisfying the following relationship:

Hm ³ > Ha ³ + Hb ³ . According to the capacity control type rotary compressor 80 of the embodiment of the present invention, in the S mode in which the second compression chamber 13b is deactivated, the low pressure gas sucked from the intake pipe 41 flows only into the first compression chamber 13a. Therefore, the suction efficiency of the first compression chamber 13a is improved, and the efficiency of the compressor is improved.

In some examples of the invention, the thickness of the first cylinder 10a and the thickness of the second cylinder 10b are equal.

Specifically, the pressure switch communicates with the second vane chamber 15b through the intermediate partition 40.

According to some embodiments of the present invention, the opening portion of the second vane cavity 15b is connected to the deformable sealing plate 16, at which time the deformation of the sealing plate 16 due to the pressure difference acting on the two planes of the sealing plate 16, The second slider 20b can be held in the second slider chamber 15b. Specifically, the deflection of the sealing plate 16 is 12 μm or more.

A refrigeration cycle apparatus according to an embodiment of the present invention includes a capacity control type rotary compressor, a condenser, an expansion device, and an evaporator according to the above embodiment of the present invention.

It should be noted that the connection relationship between the capacity control type rotary compressor, the condenser, the expansion device, and the evaporator is a prior art, and will not be described in detail herein.

Hereinafter, a capacity control type rotary compressor according to an embodiment of the present invention will be described with reference to Figs. 1 to 9, wherein the cylinder 10a refers to the first cylinder, the cylinder 10b refers to the second cylinder, and the compression chamber 13a refers to The first compression chamber, the compression chamber 13b refers to the second compression chamber, the slider 20a refers to the first slider, and the slider 20b refers to the second slider. The piston 24a refers to the first piston, the piston 24b refers to the second piston, the vane chamber 15a refers to the first vane chamber, and the vane chamber 15b refers to the second vane chamber.

Embodiments of the present invention will be described with reference to Figs. The two-cylinder capacity-controlled rotary compressor (hereinafter referred to as a rotary compressor 80) shown in Fig. 1 is composed of an electric motor 6 and a compressor structure 5 fixed to the inner diameter of the casing 1. The compression mechanism 5 is composed of a cylinder A 1 0 a and a cylinder B 1 0 b which are vertically disposed by the intermediate partition 40, a main bearing 25 and a sub-bearing 30 fixed to the upper portion thereof, a main bearing muffler 26 and a sub-bearing muffler 3 3 The eccentric shaft 7 and the like which are slidably supported by the main bearing 25 and the sub-bearing 3 Q are composed of the eccentric shaft 7 and the like. The outer circumference of the circular intermediate partition 4 Q is fixed at the inner diameter of the casing 1.

The high-pressure gas discharged from the exhaust pipe 3 of the sealed casing 1 passes through the condenser (:, the expansion valve V, the evaporator E becomes a low-pressure gas, and reaches the accumulator 70. Thereafter, the low-pressure gas is connected from the intermediate partition 4 0 The outer suction pipe (or called the suction pipe) 4 1 (Fig. 2) flows into the cylinder 10 a and the cylinder 1 0 b. The compressed high pressure gas is discharged from the main bearing muffler 26 to the casing 2 Moreover, the thickness and displacement of the two cylinders are also equivalent. However, the respective cylinder thicknesses and displacements may be appropriately changed depending on the purpose of use.

The three-way valve 50 provided on the outer side of the casing 1 is a means for stopping or releasing the compression of the cylinder 1 Q b while the rotary compressor 8 Q is in operation. The three-way valve 5 Q has three connection ports, and the high pressure port 5 Q a is connected to the high pressure pipe 5 2 which is open to the inside of the casing 1. Low pressure port 5 0 b Connect the reservoir 7 0 low pressure outlet pipe 7 2. High and low pressure port 5 0 c Connect the pressure switch tube 5 5 of the outer partition of the intermediate partition 4 0 . As will be described later, the pressure switching tube 55 is connected to the sealed vane chamber 1 5 b to switch the pressure of the chamber between high pressure and low pressure. The inside of the three-way valve 50 has a slider 5 7 that can slide. The slider 5 7 is driven by an electromagnetic coil (not shown) constituting the three-way valve 50. Alternatively, a four-way valve can be used in place of the three-way valve.

The P-mode of Fig. 1 is at the position where the slider 57 is open to the high and low pressure ports 50c, so the pressure of the pressure switching tube 5 connected thereto is a high pressure (Pd) equivalent to the internal pressure of the casing 1. Capacity-controlled rotary compressor 8 0 When two cylinders start to compress, they can achieve a cooling capacity of 1 Q 0 %. The 1 Q 0 % of the behavior P mode.

On the other hand, when the slider 57 is moved to the S-mode of Fig. 1 by control, the pressure switching tube 5 5 is a low pressure (P s ) equal to the pressure of the low pressure outlet pipe 7 2 . At this time, the compression of the cylinder 1 Q b in the rotary compressor 80 is stopped, so the cooling capacity is reduced to 50%. This run is called S mode. In this way, the rotary compressor in operation with the capacity control function is controlled by the three-way valve 50, and the mode can be switched between the P mode and the S mode.

The pressure of the pressure switching tube 5 5 of Fig. 2 is the high pressure (P d ), so the P mode is in operation. Cylinder A

In the compression chamber 1 3 a and the compression chamber 1 3 b provided in each of the 10 a and the cylinder B 1 0 b, the piston 2 4 a and the piston 2 4 b revolve. The slider 20 a and the slider 2 0 b abutting the outer diameters of these pistons are machined in the cylinder The inside of the slider groove reciprocates. In addition, the back of these sliders is composed of a slider chamber 15a and a slider chamber 15b.

The upper end of the vane chamber 1 5 a having the vane spring 2 1 a is open to the casing 1, so that the pressure is on the high pressure side. On the other hand, the upper end opening surface of the slider chamber 15b is sealed at the intermediate partition 40, and the lower end opening surface is sealed by the sealing plate 16 fixed by the rivet 18. In addition, the vane chamber 1 5 b abolishes the vane spring. The suction hole processed in the intermediate partition 4 0 4 is inhaled into the suction pipe 4 1. Connect the low pressure outlet pipe 7 of the accumulator 70. The tip end portion of the suction hole 45 is provided with an inclined hole 4 3 a and an inclined hole 4 3 b which are respectively opened to the compression chamber 1 3 a and the compression chamber 1 3 b.

In Fig. 2, the pressure switching tube 5 5 is a high pressure (P d ), so that the sliding piece 2 0 b and the sliding piece 20 a are respectively abutted against the piston in a phase of 1 8 Q degrees, and the compression chamber 13 is reciprocated. a and the compression chamber 1 3 b perform the usual compression (P mode). In the P mode, the low-pressure gas flowing from the accumulator 7 Q to the intake hole 4 5 of the intermediate partition 4 Q is equally branched to the inclined hole 4 3 a and the inclined hole 4 3 b of the two cylinder openings, respectively. The compression chamber 13 3 a and the compression chamber 1 3 b are compressed. Thereafter, it is discharged to the main bearing muffler 26 and the sub-bearing muffler 3 3 . The high-pressure gas discharged from the sub-bearing muffler 3 3 is discharged to the lower portion of the motor 6 through the communication hole 28 and the high-pressure gas of the main bearing muffler 26.

In order to reduce the intake resistance of the low-pressure gas and improve the intake efficiency, it is necessary to enlarge the inner diameter of the intake hole 45 as compared with the conventional capacity-controlled compressor. In order to satisfy this necessary condition, the present invention has been designed as follows.

Hm ³ > Ha ³ + Hb ³ As shown in Fig. 2, Hm is the thickness of the intermediate partition 40, and Ha and Hb are the thicknesses of the cylinder A 1 0 a and the cylinder A 1 0 a, respectively. Here, the pressure loss (Δ P ) of the piping is proportional to the third power of the pipe inner diameter and the first power of the pipe length. This is determined by the Fanning formula derived from the theorem. In addition, the total length of the intake circuit including the accumulator is not different from the conventional design, that is, the case where the intake pipe is connected to the cylinder.

According to the above inequality, the reason for replacing the suction pipe or the suction hole, the thickness of the partition plate 40 in use, and the thickness of each cylinder is that the present invention does not need to respectively connect the suction pipe of the cylinder, and one suction pipe can be connected to the intermediate partition 40. Further, the inner diameter of the suction hole or the outer diameter of the suction pipe cannot be larger than the thickness of the cylinder or the intermediate partition. That is, the thickness of the cylinder or the intermediate partition may be substituted as the inner diameter of the suction pipe or the outer diameter of the suction hole. Moreover, an embodiment of the present invention is Ha = Hb.

In the present invention, since the suction hole 45 is disposed in the intermediate partition 4 Q, the inner diameter thereof is easily enlarged. As a case, if Ha = Hb = 1 5 m m and Hm = 2 0 m m, the pressure loss (A P ) is improved by about 19%. The improvement effect can improve the inhalation efficiency of the P mode and the S mode described later.

In Figs. 3 and 4, the pressure switching tube 5 5 pressed into the side surface of the intermediate partition 4 Q opens through the vertical hole 48 to the closed sliding vane chamber 15b. Therefore, according to the pressure of the pressure switching tube 5 5 , the pressure of the vane chamber 1 5 b can be Switch. In the conventional design, since the pressure switching tube is directly pressed into the sliding chamber having a low rigidity, there is a problem that the cylinder is deformed. On the other hand, in the present invention, the pressure switching tube 55 can be press-fitted into the intermediate partition 40 having a high rigidity, so that the above problem can be solved.

Next, in Fig. 5, the pressure of the pressure switching tube 5 5 is a low pressure (P s ), so that the S mode is in operation. At this time, the slider 2 0 b is stationary in the slider chamber 15b at the top dead center, and the piston 24b is idling inside the compression chamber 13b. Therefore, the pressure of the compression chamber 1 3 b is switched to the low pressure (P s ), and the vent hole 3 4 b (Fig. 6) is closed by the exhaust valve.

Figure 6 shows the stationary state of the slider 2 0 b. Usually, the difference between the slider height (right angle to the sliding direction) and the cylinder slot height (gap) is the cylinder thickness (H b ) of 0. 5~ 0 . 8 / 1 0 0 0. For example, if H b = 1 5 mm, the above gap is 7.5 to 1 2 μ m. Sealing plate 1 6. It can be an elastic sheet such as Swedish steel. When the vane chamber 1 5 b is switched to the low pressure ( P s ), it is designed to be deflected by more than 12 μm depending on the difference from the high pressure (P d ) of the casing 1. As a result, due to the deformation of the sealing plate 16, the slider 20b is held in the slider chamber 15b, and the S mode continues. Due to the control of the three-way valve, if the pressure of the vane chamber 15b is switched to the high pressure (Pd), the sealing plate 16 is not deformed, so the vane 2 0 b can be released from rest and switched to the P mode.

Figure 7 shows the flow of the suction gas in the S mode. The low-pressure gas flows from the accumulator 70 to the suction port 45, flows only into the inclined hole 4 3 a , and is compressed in the compression chamber 13 3 a. Thereafter, the high pressure gas can be discharged from the main bearing muffler 26 to the lower portion of the motor 6. In terms of the flow of the suction gas, the compression chamber 1 3 a monopolizes the low-pressure gas flowing into the suction port 45, so that the amount of the suction gas in the compression chamber 13 3a increases. Therefore, the suction efficiency can be improved and the cooling capacity can be improved.

Fig. 8 and Fig. 9 show a comparison between the conventional design in which two cylinders are connected to the suction pipe and the comparison of the present invention in the intermediate partition 4 Q in terms of the cooling capacity and C 0 P. In these figures, the left side is the data of the previous design, and the right side is the data of the present invention. In addition, the performance of the conventional design in the P mode is 1 . Q 0 (reference) to indicate the performance of the S mode. Further, as described above, when H a = H b = l 5 mm and Hm = 20 mm, the inner diameter of the cylinder suction hole is 1 3 mm and 18 mm, respectively.

In Fig. 8, the cooling capacity S mode of the present invention was confirmed to be 12%, and the P mode was improved by 3.6%. In Figure 9, it is confirmed that the C 0 P of the present invention is improved in the S mode by 3.6 % and the P mode is 2.4%. The reason why the improvement in the cooling capacity of the S mode is large is that, as described above, the compression chamber 13 3 can monopolize a sufficient amount of intake air. However, the reason why the COP is only 3.6 % is that the input power increases as the inspiratory volume increases. On the other hand, in terms of the cooling capacity of the P mode and the improvement of C 0 P, the resistance loss (Δ Ρ ) of the suction gas can be reduced as the suction hole 45 is enlarged. Here, the C 0 P increase in the S mode is very important. In terms of the annual operating rate of the air conditioner, the S mode is about 3 times that of the P mode, so the 3. 6 % C 0 P improvement can be improved by APF evaluation. %the above.

In the above-described technical disclosure, the cylinder A 1 Q a is disposed between the intermediate partition 4 Q and the main bearing 25, and the cylinder B 1 0 b is disposed between the intermediate partition 40 and the sub-bearing 30. On the contrary, the cylinder B 1 0 b is disposed between the intermediate partition 40 and the main bearing 25, and the cylinder A 1 0 a may be disposed between the intermediate partition 4 Q and the sub-bearing 3 Q.

In addition, one of the two cylinders is a slide-swing type rotary compression mechanism in which the piston and the slide are integrated, and the other cylinder is a slide-reciprocating rotary compression mechanism in which the piston and the slide are separated. The compression and compression of the compression chamber can also be controlled to achieve the effects and effects of the present invention. Further, the above-described technique has been described with reference to a vertical rotary compressor in which the eccentric shafts are arranged in the vertical direction, but it is also applicable to a horizontal rotary compressor in which the eccentric shafts are arranged horizontally.

The capacity-controlled rotary compressor to which the efficiency improvement technique of the present invention is applied can be widely applied to household air conditioners, commercial air conditioners, or water heaters and refrigeration units.

The present invention relates to a capacity-controlled rotary compressor in which a compression chamber is deactivated during operation or a cylinder is deactivated during operation to make a refrigeration capacity variable in a rotary compressor having two cylinder compression chambers. related. Further, as shown in [Patent Document 2] and [Patent Document 3], the present invention employs a "sliding chamber pressure switching method" for switching the sealed vane chamber pressure between high pressure and low pressure. The present invention is characterized in that an intermediate hole having an inner diameter is provided in the intermediate partition provided between the two cylinders, and the main purpose is to improve the suction efficiency, thereby improving the efficiency of the compressor.

The twin-cylinder capacity-controlled rotary compressor of the present invention can be applied to an air conditioner, a refrigerating and freezing machine, a water heater, etc., and various refrigerants can be used. In addition to the fixed speed motor, it can also be mounted on a variable frequency motor to expand the range of refrigeration capacity control.

In the description of this specification, reference is made to the terms "one embodiment", "some embodiments", "example",

The description of the "specific examples", or "some examples" and the like are intended to be included in the particular features, structures, materials or features described in connection with the embodiments or examples. In the present specification, the schematic representation of the above terms is not necessarily directed to 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. In addition, various embodiments or examples described in the specification, as well as features of various embodiments or examples, may be combined and combined without departing from the scope of the invention.

Although the embodiments of the present invention have been shown and described, it is understood that the above described embodiments are illustrative and are not to be construed as limiting the scope of the invention. The embodiments are subject to variations, modifications, substitutions and variations.

Claims

claims

1. A capacity-controlled rotary compressor, characterized by including:

Sealed housing;

An electric motor, the electric motor is located in the sealed housing;

A rotary compression mechanism, which is located in the sealed housing and connected to the electric motor. The rotary compression mechanism includes: each having a first compression chamber and a second compression chamber. The first cylinder and the second cylinder of the chamber; a middle partition plate provided between the first cylinder and the second cylinder, and the middle partition plate has a pressure chamber for the first compression chamber and the second pressure chamber. a suction hole opening in the contraction chamber; a first piston and a second piston respectively revolving in the first compression chamber and the second compression chamber; with the respective rotation of the first piston and the second piston The first slide plate and the second slide plate are revolving and can perform reciprocating motion, and the second cylinder has a second slide plate cavity that accommodates the back of the second slide plate; the second slide plate is sealed A pressure switch that switches the pressure of the tablet chamber between two different pressures to stop or unstop the compression of the second cylinder, wherein the middle partition plate is connected to the suction pipe;

The thickness of the middle partition is Hm, the thickness of the first cylinder is Ha, and the thickness of the second cylinder is Hb, satisfying the following relationship:

Hm ³ > Ha ³ + Hb ³ .

2. The capacity-controlled rotary compressor according to claim 1, wherein the thickness of the first cylinder is equal to the thickness of the second cylinder.

3. The capacity-controlled rotary compressor according to claim 1 or 2, wherein the pressure switch is connected to the second sliding vane chamber through the middle partition plate.

4. The capacity-controlled rotary compressor according to any one of claims 1 to 3, characterized in that, the opening part of the second slide chamber is connected to a deformable sealing plate to seal the second The slide is retained in the second slide cavity.

5. The capacity-controlled rotary compressor according to claim 4, wherein the deflection of the sealing plate is 12 μm or more.

6. The capacity-controlled rotary compressor according to any one of claims 1 to 5, characterized in that the pressure switch is a three-way valve or a four-way valve.

7. A refrigeration cycle device, including the capacity-controlled rotary compressor according to any one of claims 1-6.