JP2009074445A - Two-cylinder rotary compressor and refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high-performance, high-capability two-cylinder rotary compressor that can obtain a sufficient inertia supercharging effect with a suppressed influence of pulsation to other cylinder chamber mutually by reducing thicknesses of cylinders and an intermediate partition plate and providing in parallel mutually independent suction passages to the intermediate partition plate, and improve a maximum capability without increasing a discharging volume of the cylinder chambers, and to provide a refrigerating cycle device capable of improving refrigerating cycle efficiency using the two-cylinder rotary compressor. <P>SOLUTION: The two-cylinder rotary compressor (A) is configured to house an electric motor portion 3 and a compressing mechanism portion 3 coupled with each other via a rotating shaft 4 inside a sealed case 1. The compressing mechanism portion is provided via the intermediate partition plate 7, at both end faces, with a first cylinder 8A having a first cylinder chamber 14a and a second cylinder 8B having a second cylinder chamber 14b. The intermediate partition plate includes two independent suction passages 15a and 15b. Each of the suction passages communicates with only either one of the first cylinder chamber and the second cylinder chamber. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a two-cylinder rotary compressor having two cylinder chambers, and a refrigeration cycle apparatus that constitutes a refrigeration cycle using the two-cylinder rotary compressor.

  Various types of compressors are used in a refrigeration cycle apparatus including a refrigeration cycle circuit. For example, a two-cylinder rotary compressor is frequently used in an air conditioner. In this type of two-cylinder rotary compressor, an electric motor part and a compression mechanism part are accommodated in a sealed case, and the electric motor part and the compression mechanism part are connected via a rotating shaft.

  In the compression mechanism portion, the rotation shaft is provided eccentrically between the main shaft portion pivotally supported by the main bearing, the sub shaft portion pivotally supported by the sub bearing, and the main shaft portion and the sub shaft portion. Two crankshaft parts with which the roller is fitted are provided. The two crankshaft portions are provided with a phase difference of 180 ° from each other.

  Each crankshaft portion and the roller are accommodated in the cylinder chambers of two cylinders configured separately so as to be eccentrically rotatable. That is, the compression action is performed in the two cylinder chambers with a phase difference of about 180 ° from each other. An intermediate partition plate is interposed between these cylinders, and a portion between the crankshaft portions faces the intermediate partition plate.

  By the way, in the conventional compressor, a suction passage is provided penetrating in the radial direction from the outer peripheral surface of each cylinder toward the inner diameter portion, and the cylinder chamber and the suction side refrigerant pipe are communicated with each other through the suction passage. That is, it is an “independent suction type” in which each suction side refrigerant pipe communicates with the suction passage of each cylinder and sucks and guides the refrigerant.

  In general, in a rotary compressor, when the discharge stroke ends and is switched to the suction stroke, there is an extremely instantaneous interval (blank period), and the refrigerant flow stops. Further, with the start of the suction stroke, the volume of the suction chamber increases rapidly, and a refrigerant flow is generated due to the pressure difference. As a result, pulsation is also present in the rotary compressor, although not as remarkable as in the reciprocating (reciprocating) compressor.

  Based on this pressure pulsation, the supercharging effect of increasing the refrigeration capacity at a predetermined operating frequency can be obtained by appropriately setting the length of the suction pipe and the like. Therefore, if the supercharging effect is obtained in the high rotation range where the operation frequency is high, the refrigeration capacity range can be expanded.

  In such a rotary compressor, in order to reduce the leakage loss of the refrigerant and improve the compression efficiency, the leakage from the roller outer peripheral surface having the largest leakage at the sliding portion and the cylinder inner peripheral surface should be reduced. Therefore, it is preferable to reduce the thickness (axial length) of the cylinder to be smaller.

However, if the thickness of each cylinder is made extremely small, it becomes impossible to secure a sufficient cross-sectional area of the suction passage provided in the cylinder, and conversely, the suction loss increases and the performance deteriorates.
In contrast to the independent suction type in the above-described two-cylinder rotary compressor, for example, [Patent Document 1] and [Patent Document 2] disclose a two-cylinder rotary compressor having a branch suction type suction passage. Yes.
JP-A-9-250477 Japanese Patent No. 3869705

  The suction passages in these patent documents are provided in an intermediate partition plate interposed between the first cylinder and the second cylinder. That is, the opening end of the suction passage is provided on the outer peripheral surface of the intermediate partition plate, and the refrigerant pipe is connected. The suction passage is branched into two inside the intermediate partition plate, and the end of each branch passage opens into a cylinder chamber formed in each cylinder inner diameter.

  In the branched suction type compressor, the thickness of the intermediate partition plate can be increased to ensure a sufficient sectional area of the suction passage. On the other hand, the refrigerant gas is guided from the outside of the compressor to the two cylinder chambers through one suction passage and two branch passages. In other words, the suction port provided in each cylinder chamber communicates with one suction passage through two branch passages.

  Further, the compression action is performed with a phase difference of about 180 ° in each cylinder chamber, and since each cylinder chamber communicates with one suction passage, pressure pulsation generated based on the compression action of each cylinder chamber is generated. It was suppressed by canceling each other in the suction passage, and it was not possible to obtain a sufficient supercharging effect in the high rotation range accompanying the pressure pulsation.

  The present invention has been made on the basis of the above circumstances. The object of the present invention is to reduce the thickness of the cylinder and to arrange the independent suction passages in the intermediate partition plate in parallel with each other so that the other cylinder chambers are arranged. This is a high-performance, high-capacity two-cylinder rotary compressor capable of preventing the suppression of pulsation and improving the maximum capacity without increasing the displacement volume of the cylinder chamber. An object of the present invention is to provide a refrigeration cycle apparatus that uses a cylinder rotary compressor to improve the refrigeration cycle efficiency.

In order to satisfy the above object, the two-cylinder rotary compressor of the present invention accommodates an electric motor part and a compression mechanism part connected via a rotary shaft in a sealed case, and the compression mechanism part is interposed via an intermediate partition plate. A first cylinder having a first cylinder chamber and a second cylinder having a second cylinder chamber are provided on both end faces of the lever, and two independent suction passages are provided in parallel on the intermediate partition plate. Each suction passage communicates with only one of the first cylinder chamber and the second cylinder chamber.
To satisfy the above object, the refrigeration cycle apparatus of the present invention is connected so that the above-described two-cylinder rotary compressor, the condenser, the expansion device, and the evaporator constitute a refrigeration cycle through a refrigerant pipe. Is done.

  According to the present invention, a sufficient inertial supercharging effect can be obtained, the maximum capacity can be improved without increasing the excluded volume of the cylinder chamber, and a high-performance, high-capacity two-cylinder rotary compressor and the two-cylinder rotation A refrigeration cycle apparatus that improves the refrigeration cycle efficiency using a compressor can be provided.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional structure of a two-cylinder rotary compressor A and a schematic configuration diagram of a refrigeration cycle apparatus R including the two-cylinder rotary compressor A. (Note that, in order to avoid complications in the drawings, components that are not denoted by reference numerals are not illustrated or illustrated, but are not denoted by reference numerals in the drawings. same as below)
First, the configuration of the refrigeration cycle apparatus R will be described. A two-cylinder rotary compressor A, a condenser B, an expansion device C, an evaporator D, and a gas-liquid separator E are provided. The refrigerant pipe P is communicated. As will be described later, the refrigerant gas compressed by the two-cylinder rotary compressor A is discharged to the refrigerant pipe P and circulates in the order of the above components to form a refrigeration cycle, and is sucked into the two-cylinder rotary compressor A again. It has come to be rare.

Next, the two-cylinder rotary compressor A will be described in detail.
In the figure, reference numeral 1 denotes a sealed case. A compression mechanism 2 is provided at the lower part of the sealed case 1, and an electric motor part 3 is provided at the upper part. The compression mechanism unit 2 and the electric motor unit 3 are connected via a rotating shaft 4.

  For example, a brushless DC synchronous motor (which may be an AC motor or a commercial motor) is used for the electric motor unit 3, and a stator 5 that is press-fitted and fixed to the inner surface of the sealed case 1 and a predetermined gap inside the stator 5 exist. And a rotor 6 fitted to the rotating shaft 4.

  The compression mechanism unit 2 includes an intermediate partition plate 7, and a first compression mechanism unit 2 </ b> A and a second compression mechanism unit 2 </ b> B provided on both end surfaces of the intermediate partition plate 7. The first compression mechanism 2A is formed on the upper surface side of the intermediate partition plate 7 and includes a first cylinder 8A. The second compression mechanism 2B is formed in the lower part on the lower surface side of the intermediate partition plate 7, and includes a second cylinder 8B.

  The first cylinder 8A is press-fitted and fixed to the inner peripheral surface of the sealed case 1, and the main bearing 11 is superimposed on the upper surface portion and fixed via a mounting bolt. The auxiliary bearing 12 and the valve cover are overlapped on the lower surface portion of the second cylinder 8B, and are attached and fixed to the intermediate partition plate 7 via attachment bolts.

  A portion of the rotating shaft 4 pivotally supported by the main bearing 11 is referred to as a main shaft portion 4a, and a portion pivotally supported by the auxiliary bearing 12 which is the lowermost end of the rotating shaft 4 is referred to as a subshaft portion 4b. Further, crankshaft portions 4c and 4d are integrally provided at positions penetrating the insides of the first cylinder 8A and the second cylinder 8B of the rotary shaft 4, respectively. A connecting portion between the crankshaft portions 4 c and 4 d faces the intermediate partition plate 7.

  The crankshaft portions 4c and 4d are formed to be eccentric from each other by the same amount from the central axes of the main shaft portion 4a and the subshaft portion 4b of the rotating shaft 4 with a phase difference of about 180 ° and have the same diameter. A first roller 13a is fitted to the crankshaft portion 4c, and a second roller 13b is fitted to the crankshaft portion 4d. The first and second rollers 13a and 13b are formed to have the same outer diameter.

  Upper and lower surfaces of the inner diameter portions of the first cylinder 8A and the second cylinder 8B are partitioned by the main bearing 11, the intermediate partition plate 7, and the auxiliary bearing 12. A first cylinder chamber 14a is formed in the inner diameter portion of the first cylinder 8A, and a second cylinder chamber 14b is formed in the inner diameter portion of the second cylinder 8B.

  The first roller 13a is accommodated in the first cylinder chamber 14a so as to be eccentrically rotatable, and the second roller 13b is accommodated in the second cylinder chamber 14b so as to be eccentrically rotatable. The first and second rollers 13a and 13b have a phase difference of 180 ° from each other, and part of the circumferential surfaces along the respective axial directions can rotate eccentrically while making line contact with the circumferential walls of the cylinder chambers 14a and 14b.

  The first and second cylinders 8A and 8B are provided with blade chambers, and blades and spring members are accommodated in the respective blade chambers. The spring member is a compression spring, and an elastic force (back pressure) is applied to the blade to bring the tip edge into line contact along the axial direction of the peripheral surfaces of the rollers 13a and 13b. Therefore, the blade reciprocates along the blade chamber, and the cylinder chambers 14a and 14b are divided into two chambers regardless of the rotation angles of the rollers 13a and 13b.

  The main bearing 11 and the sub-bearing 12 are provided with a discharge valve mechanism, which communicates with the cylinder chambers 14a and 14b and is covered with a valve cover. As will be described later, the discharge valve mechanism is opened in a state where the refrigerant gas compressed in each of the cylinder chambers 14a and 14b has risen to a predetermined pressure. The compressed refrigerant gas is discharged from the cylinder chambers 14 a and 14 b into the valve cover, and further guided into the sealed case 1.

The intermediate partition plate 7 interposed between the first cylinder 8A and the second cylinder 8B has a first suction passage which is two suction passages from the outer peripheral surface toward the axial direction. 15a and the 2nd suction passage 15b are arranged in parallel. (In FIG. 1, only the second suction passage 15b is shown. The first suction passage 15a is provided on the back side.)
Next, the first suction passage 15a and the second suction passage 15b and the peripheral structure thereof will be described in detail.
FIG. 2 is a plan view of the intermediate partition plate 7, and FIG. 3 is a side view of the two-cylinder rotary compressor A and the gas-liquid separator E.

  A first suction refrigerant pipe Pa and a second suction refrigerant pipe Pb, which are two refrigerant pipes in the vertical direction from the bottom of the gas-liquid separator E, are provided in parallel. These first and second refrigerant tubes Pa and Pb are bent in the horizontal direction at the same height L from the bottom of the sealed case 1 of the compressor A.

  Each refrigerant pipe Pa, Pb passes through a through hole 17 provided in the sealed case 1 of the compressor A as shown in FIG. 1, and the first pipe provided in the intermediate partition plate 7 as shown in FIG. Are connected to the gas suction ports a and b of the second suction passage 15a or the second suction passage 15b, respectively.

  In other words, the first suction passage 15a and the second suction passage 15b provided in the intermediate partition plate 7 are provided with gas suction ports a and b on the outer peripheral surface of the intermediate partition plate 7, respectively. As shown in FIG. 3, the gas suction ports a and b are provided at the same height L from the bottom of the sealed case 1, so that the axial positions of the compressor A substantially coincide with each other.

  The first suction passage 15a is provided obliquely above the upper end surface of the intermediate partition plate 7 at a substantially middle portion between the gas suction port a to which the first suction refrigerant pipe Pa is connected and the inner diameter portion. The gas outlet c is opened.

The second suction passage 15b is provided obliquely downward at a substantially intermediate portion between the gas suction port b and the inner diameter portion to which the second suction refrigerant pipe Pb is connected, and is formed on the lower end surface of the intermediate partition plate 7. The gas outlet port d is opened.
The gas outlet c of the first suction passage 15a communicates with a notch 16a provided in the inner diameter portion of the first cylinder 8A. The notch 16a opens to a first cylinder chamber 14a formed in the inner diameter portion of the cylinder 8A, and serves as a suction port 16a for the first cylinder chamber 14a.

  The gas outlet port d of the second suction passage 15b communicates with a notch 16b provided in the inner diameter portion of the second cylinder 8B. This notch 16b opens to a second cylinder chamber 14b formed in the inner diameter portion of the cylinder 8B, and serves as a suction port 16b for the second cylinder chamber 14b.

  That is, the first and second suction passages 15 a and 15 b provided side by side with the intermediate partition plate 7 include gas suction ports a and b on the outer peripheral surface of the intermediate partition plate 7, respectively. The first suction passage 15a communicates with the suction port 16a of the second cylinder chamber 14b through a gas outlet c provided in the upper end surface of the intermediate partition plate 7. The second suction passage 15b communicates with the suction port 16b of the second cylinder chamber 14b through a gas outlet port d provided on the lower end surface of the intermediate partition plate 7.

  In the two-cylinder rotary compressor A configured as described above, when the electric motor unit 3 is energized, the rotary shaft 4 is rotationally driven, the first roller 13a moves eccentrically in the first cylinder chamber 14a, and the first The second roller 13b moves eccentrically in the second cylinder chamber 14b. Each of the cylinder chambers 14a and 14b is divided into two chambers by a blade, and the refrigerant gas separated by the gas-liquid separator E is sucked into the one chamber through the refrigerant pipes Pa and Pb.

  More specifically, the refrigerant gas separated by the gas-liquid separator E is sucked into the second cylinder chamber 14b from the first refrigerant pipe Pa via the first suction passage 15a provided in the intermediate partition plate 7. It is. The refrigerant gas separated by the gas-liquid separator E is sucked into the second cylinder chamber 14b from the second refrigerant pipe Pb through the second suction passage 15b provided in the intermediate partition plate 7.

Since the crankshaft portions 4c and 4d provided on the rotary shaft 4 are formed so as to have a phase difference of 180 ° from each other, the refrigerant gas is sucked into the first cylinder chamber 14a from the first suction passage 15a. The timing at which the refrigerant gas is sucked into the second cylinder chamber 14b from the second suction passage 15b also has a phase difference of approximately 180 °.
The first roller 13a moves eccentrically in the first cylinder chamber 14a, the second roller 13b moves eccentrically in the second cylinder chamber 14b, and the discharge valve mechanism side provided in each cylinder chamber 14a, 14b. The volume of the chamber decreases, and the pressure increases accordingly.

  When the volume of the chamber on the discharge valve mechanism side reaches a predetermined volume, the refrigerant gas compressed in this chamber rises to a predetermined pressure. At the same time, the discharge valve mechanism is opened, and the compressed and high-temperature and high-pressure refrigerant gas is discharged into the valve cover. The timing at which the compressed refrigerant gas is discharged to the discharge valve mechanism also has a phase difference of approximately 180 °.

  The compressed refrigerant gas is led out from each valve cover directly or indirectly to the space between the compression mechanism 2 and the motor 3 in the sealed case 1. Then, the motor part is circulated through gaps formed between the rotating shaft 4 and the rotor 6 constituting the motor part 3, between the rotor 6 and the stator 5, between the stator 5 and the inner peripheral wall of the sealed case 1, and the like. 3 fills the space inside the sealed case 1 formed on the upper side.

  The compressed refrigerant gas is led from the two-cylinder rotary compressor A to the refrigerant pipe P, led to the condenser B to be condensed and liquefied, led to the expansion device C and adiabatically expanded, and led to the evaporator D. It evaporates and takes away the latent heat of evaporation from the surroundings to produce a freezing action. The evaporated refrigerant is guided to the gas-liquid separator E for gas-liquid separation, and only the gas component is sucked into the compression mechanism 2 of the two-cylinder rotary compressor A and compressed again.

As described above, the first cylinder 8A having the first cylinder chamber 14a is provided on one end face of the intermediate partition plate 7, and the second cylinder 8B having the second cylinder chamber 14b on the other end face. Is provided.
The intermediate partition plate 7 is provided with two independent suction passages 15a and 15b, the first suction passage 15a communicates only with the first cylinder chamber 14a, and the second suction passage 15b is the second suction passage. It was made to communicate only with the cylinder chamber 14b.

  Accordingly, the thickness of the first cylinder 8A and the thickness of the second cylinder 8B are made as small as possible, the leak in the clearance between the first roller 13a and the first crankshaft portion 4c, and the second roller Leakage in the clearance between 13b and the second crankshaft portion 4d is reduced. The sliding loss around the blades provided in the respective cylinder chambers 14a and 14b is reduced, and the compression performance is improved.

  Further, since the first suction passage 15a and the second suction passage 15b are provided in the intermediate partition plate 7 independently of each other, the pulsation that is inevitably generated in the two-cylinder rotary compressor A can be prevented, and the suction pipe A sufficient supercharging effect can be obtained particularly in a high rotation range by appropriately setting the length of the engine.

  Further, the gas suction port a of the first suction passage 15a and the gas suction port b of the second suction passage 15b are provided on the outer peripheral surface of the intermediate partition plate 7 so that the axial positions thereof are substantially coincident with each other. Therefore, the first suction passage 15a and the second suction passage 15b can be provided with the thickness of the intermediate partition plate 7 being minimized.

The connection between the first suction passage 15a and the gas-liquid separator E by the first suction refrigerant pipe Pa is facilitated, and the second suction passage 15b and the gas-liquid separator by the second suction refrigerant pipe Pb. Connection with E becomes easy.
The distance between the main bearing 11 and the sub-bearing 12 mounted with the intermediate partition plate 7 and the first and second cylinders 8A and 8B interposed therebetween is minimized, and the maximum axial load on the main bearing 11 and the sub-bearing 12 is maximized. Increase in value can be suppressed.
That is, when the intermediate partition plate 7 is thickened, the distance between the main bearing 11 and the sub-bearing 12 attached with the intermediate partition plate 7 and the two cylinders 8A and 8B interposed therebetween increases. Although the maximum value of the axial load increases, the increase in the maximum value of the axial load applied to the main bearing 11 and the auxiliary bearing 12 can be suppressed by minimizing the thickness of the intermediate partition plate 7.

To summarize the above, a high-performance two-cylinder rotary compressor A can be obtained while ensuring high performance. And the refrigerating-cycle efficiency can be improved by employ | adopting the above-mentioned 2-cylinder rotary compressor A and comprising the refrigerating-cycle apparatus R. FIG.
If the materials or thicknesses of the first and second suction refrigerant tubes Pa and Pb are made different from each other, the difference in natural frequency between the first and second suction refrigerant tubes Pa and Pb increases. Abnormal resonance of the tubes Pa and Pb can be prevented.

In the above embodiment, as shown in FIG. 2, the gas outlet c of the first suction passage 15a provided in the intermediate partition plate 7 and the gas outlet d of the second suction passage 15b are shifted from each other. However, the present invention is not limited to this.
FIG. 4 is a plan view of the intermediate partition plate 7 in the second embodiment.

Here, the gas suction port a of the first suction passage 15a and the gas suction port b of the second suction passage 15b are provided so that their axial positions are substantially coincident with each other. It is installed side by side.
A gas outlet c provided at the tip of the first suction passage 15 a is opened at the upper end surface of the intermediate partition plate 7, and a gas outlet d provided at the tip of the second suction passage 15 b is provided on the intermediate partition plate 7. Opened at the lower end surface. However, the gas outlets c and d are provided so as to be inclined with respect to each other so that their center coordinate positions O substantially coincide.

The gas outlet c of the first suction passage 15a is communicated with the suction port 16a of the first cylinder chamber 14a, and the gas outlet d of the second suction passage 15b is connected to the suction port 16b of the second cylinder chamber 14b. There is no change in being communicated to.
Therefore, by adopting such a configuration, the effects described above can be obtained, and the compression start positions in the first cylinder chamber 14a and the second cylinder chamber 14b can be made the same, thereby sharing the design. And productivity can be improved.

Further, a two-cylinder rotary compressor A as described below can be configured on the premise that suction passages 15a and 15b that are independent from each other are provided in the intermediate partition plate 7.
FIG. 5 is a side view of a two-cylinder rotary compressor and a gas-liquid separator in the third embodiment, and FIG. 6 is a cross-sectional view and a refrigeration cycle of a two-cylinder rotary compressor according to a modification of the third embodiment. FIG. 7 is an exploded perspective view of a main part of a compression mechanism portion applied to any two-cylinder rotary compressor.

First, from FIG. 5, the first suction refrigerant pipe Pa that communicates the gas-liquid separator E and the first suction passage 15 a provided in the intermediate partition plate 7 of the two-cylinder rotary compressor A is as follows. It is configured exactly as described.
However, a three-way switching valve 20 is provided in the middle of the second suction refrigerant pipe Pb that communicates the gas-liquid separator E and the second suction passage 15b provided in the intermediate partition plate 7. In other words, the second suction refrigerant pipe Pb extending from the bottom of the gas-liquid separator E is connected to the first port of the three-way switching valve 20. A second suction refrigerant pipe Pb communicating with the second suction passage 15b is connected to the second port of the three-way switching valve 20.

  Connected to the third port of the three-way switching valve 20 is a bypass pipe Pc that is branched from the refrigerant pipe P protruding from the upper end of the two-cylinder rotary compressor A. Therefore, the three-way switching valve 20 can switch and guide the low-pressure refrigerant gas led out from the gas-liquid separator E to the second suction passage 15b via the second refrigerant pipe Pb, and also the two-cylinder rotary compressor A. Thus, a part of the high-pressure refrigerant gas compressed and discharged to the condenser B can be switched and guided directly from the bypass pipe Pc to the second suction passage 15b.

  On the other hand, there is no additional material in the first suction passage 15a. Therefore, the low-pressure refrigerant gas separated by the gas-liquid separator E is always first through the first suction refrigerant pipe Pa. It is led to the suction passage 15a.

The two-cylinder rotary compressor A shown in FIG. 6 is exactly the same as that described above, and only the main components are given the same reference numerals and a new description is omitted. The components of the refrigeration cycle apparatus R are also the same, and the same components are denoted by the same reference numerals and are not described again.
The first suction refrigerant pipe Pa extending from the gas-liquid separator E is connected to the first suction passage 15a without change. The second suction refrigerant pipe Pb is connected to the second suction passage 15b, and an on-off valve 22 is provided in the middle portion. Further, a bypass pipe Pc is branched from the discharge side refrigerant pipe P that communicates the two-cylinder rotary compressor A and the condenser B.

  The bypass pipe Pc is connected to a second suction refrigerant pipe Pb that communicates the gas-liquid separator E and the second suction passage 15b. In detail, it connects to the site | part between the said on-off valve 22 provided in the 2nd suction refrigerant pipe Pb, and the gas suction port b of the 2nd suction passage 15b. A bypass opening / closing valve 23 is provided in the bypass pipe Pc.

That is, the bypass on-off valve 23 is closed and the on-off valve 22 is opened, so that the refrigerant gas separated by the gas-liquid separator E passes through the second refrigerant pipe Pb to the second suction passage 15b. Led to.
Conversely, a part of the high-pressure refrigerant gas compressed by the two-cylinder rotary compressor A and discharged to the condenser B by closing the on-off valve 22 and opening the bypass on-off valve 23. Can be switched and guided from the bypass pipe Pc to the second suction passage 15b.

On the other hand, the low-pressure refrigerant gas separated by the gas-liquid separator E is always guided to the first suction passage 15a through the first suction refrigerant pipe Pa to the first suction passage 15a. It has become.
In either case of adopting the configuration of FIG. 5 or adopting the configuration of FIG. 6, a compression mechanism section as shown in FIG. 7 is provided.

In the first compression mechanism section 2A, a blade chamber 25a is provided for the first cylinder chamber 14a formed in the first cylinder 8A, and the above-described spring member 26 and blade 27a are accommodated therein. The The spring member 26 is a compression spring and applies back pressure to the blade 27a.
As a result, the rear end of the blade 27a is always elastically pressed and urged toward the cylinder chamber 14a, so that the leading edge of the blade 27a is in line contact with the peripheral wall of the roller 13a (not shown) along the axial direction.

  On the other hand, in the second compression mechanism portion 2B, a blade chamber 25b is provided for the second cylinder chamber 14b formed in the second cylinder 8B, in which only the blade 27b is accommodated, There is no spring member. The blade chamber 25b is provided at a position exposed inside the sealed case 1, and the internal pressure of the sealed case 1 applies back pressure to the blade 27b.

The idle cylinder mechanism K with respect to the 2nd compression mechanism part 2B is comprised by the above combination, and is controlled according to an operating condition so that it may mention later.
When the refrigeration load is large, such as during startup, “full capacity operation” is performed in both the first cylinder chamber 14a and the second cylinder chamber 14b. At this time, the low-pressure refrigerant separated by the gas-liquid separator E is guided from the second suction refrigerant pipe Pb to the second cylinder chamber 14b through the second suction passage 15b.

  On the other hand, the low-pressure refrigerant separated by the gas-liquid separator E is guided to the first cylinder chamber 14a via the first suction refrigerant pipe Pa and the first suction passage 15a, and the compression action is performed. . The refrigerant gas compressed in the first cylinder chamber 14 a and having a high pressure is led out into the sealed case 1 and fills the sealed case 1.

  The inside of the sealed case 1 is increased in pressure, and a high back pressure is applied to the blade 27b of the second cylinder chamber 14b. On the other hand, the low-pressure refrigerant separated by the gas-liquid separator E as described above is guided from the second suction refrigerant pipe Pb to the second cylinder chamber 14b through the second suction passage 15b.

  The blade 27b provided in the second cylinder chamber 14b has a low-pressure atmosphere at the front end protruding into the second cylinder chamber 14b, and a high-pressure atmosphere at the rear end exposed inside the sealed case 1. Accordingly, a pressure difference is generated between the front end portion and the rear end portion of the blade 27b, and the rear end portion of the high pressure of the blade 27b is pushed and the front end portion is projected and urged toward the second cylinder chamber 14b.

  The back pressure of the spring member 26 is applied to the blade 27a provided in the first cylinder chamber 14a, and the high pressure back pressure in the sealed case 1 is applied to the blade 27b provided in the second cylinder chamber 14b. become. Eventually, the compression operation is performed in both the first cylinder chamber 14a and the second cylinder chamber 14b, and the full capacity operation is performed.

When a certain amount of time has elapsed after startup, a stable condition is obtained, so “capability half operation” is performed to reduce the capability by half.
At this time, the cylinder resting mechanism K is switched. That is, the introduction of the low-pressure refrigerant gas from the gas-liquid separator E to the second suction passage 14b is stopped, and a part of the high-pressure refrigerant gas discharged from the two-cylinder rotary compressor A is replaced. The bypass pipe Pc leads to the second cylinder chamber 14b through the second suction refrigerant pipe Pb and the second suction passage 15b.

  The second cylinder chamber 14b is filled with high-pressure refrigerant gas, and the tip of the blade 27b provided in the second cylinder chamber 14b is in a high-pressure atmosphere. On the other hand, the rear end of the blade 27b is exposed inside the sealed case 1 and is in a high-pressure atmosphere. That is, since the front end portion and the rear end portion of the blade 27b are in the same high-pressure atmosphere, no differential pressure is generated.

Even in the second cylinder chamber 14b, the roller 13b rotates eccentrically. However, the position of the blade 27b that has been pushed back by the roller 13b and then retracted does not change thereafter. Since the blade 27b does not divide the second cylinder chamber 14b into two chambers, no compression action is performed in the cylinder chamber 14b. On the other hand, in the first cylinder chamber 14a, the normal compression action is performed as described above.
Therefore, while having the first and second cylinder chambers 14a and 14b, the compression operation in the second cylinder chamber 14b is stopped and the compression operation can be performed only in the first cylinder chamber 14a. It becomes.

As described above, the first compression passage 15a and the second suction passage 15b are provided in the intermediate partition plate 7 independently of each other and provided with the cylinder resting mechanism K, so that the first compression that always performs the compression action. The mechanism unit 2A and the second compression mechanism unit 2B that switches between compression operation and stop as required can be configured, and in particular, an improvement in efficiency in the low capacity range, an expansion of the capacity range, and the like can be obtained.
Note that the present invention is not limited to the above-described embodiment as it is, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

1 is a schematic cross-sectional view of a two-cylinder rotary compressor according to an embodiment of the present invention and a configuration diagram of a refrigeration cycle apparatus. The top view of the intermediate partition plate based on the embodiment. The side view of the 2-cylinder rotary compressor and gas-liquid separator which concern on the same embodiment. The top view of the intermediate partition based on 2nd Embodiment. The side view of the 2-cylinder rotary compressor and gas-liquid separator which concern on 3rd Embodiment. The schematic sectional drawing of the two-cylinder rotary compressor which concerns on the modification of the embodiment, and the block diagram of a refrigerating-cycle apparatus. The perspective view which decomposed | disassembled the principal part of the compression mechanism part based on the embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Sealing case, 4 ... Rotating shaft, 3 ... Electric motor part, 2 ... Compression mechanism part, 7 ... Intermediate partition plate, 14a ... 1st cylinder chamber, 8A ... 1st cylinder, 14b ... 2nd cylinder chamber, 8B ... second cylinder, 15a ... first suction passage, 15b ... second suction passage, a ... gas suction port (in the first suction passage), b ... gas suction port (in the second suction passage) , C... Gas outlet (for first suction passage), d... Gas outlet for (second suction passage), K ... cylinder resting mechanism, A ... two-cylinder rotary compressor, B ... condenser, C ... Expansion device, E ... Evaporator, P ... Refrigerant pipe, R ... Refrigeration cycle device.

Claims (5)

In the sealed case, the electric motor unit and the compression mechanism unit connected through the rotating shaft are accommodated,
The compression mechanism includes an intermediate partition plate, a first cylinder provided with a first cylinder chamber on one end surface of the intermediate partition plate, and a second cylinder on the other end surface of the intermediate partition plate. A second cylinder with a chamber is provided,
In the intermediate partition plate, two independent suction passages are provided in parallel,
Each of the suction passages communicates with only one of the first cylinder chamber and the second cylinder chamber.   2. The two suction passages provided in the intermediate partition plate are provided with gas suction ports on an outer peripheral surface of the intermediate partition plate, and the gas suction ports of each other have substantially the same axial position. The two-cylinder rotary compressor as described.   The two suction passages provided in the intermediate partition plate are provided with gas outlets at both end faces of the intermediate partition plate, and the center coordinate positions of the gas outlets substantially coincide with each other. And a two-cylinder rotary compressor according to claim 2.   Either one of the first cylinder chamber and the second cylinder chamber always has a compression action, and the other one has a cylinder resting mechanism that can be switched between compression action and compression stop as necessary. The two-cylinder rotary compressor according to any one of claims 1 to 3.   A two-cylinder rotary compressor according to any one of claims 1 to 4, a condenser, an expansion mechanism, and an evaporator are connected via a refrigerant pipe to constitute a refrigeration cycle. Refrigeration cycle equipment.

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