JP5005598B2 - Two-cylinder rotary compressor and refrigeration cycle apparatus - Google Patents

Description

  The present invention includes a two-cylinder rotary compressor in which a first cylinder provided with a first cylinder chamber and a second cylinder provided with a second cylinder chamber are overlapped via an intermediate partition plate; The present invention relates to a refrigeration cycle apparatus that constitutes a refrigeration cycle using the two-cylinder rotary compressor.

  In recent years, in the rotary compressor, a two-cylinder type two-cylinder rotary compressor including two sets of cylinders at the top and bottom is being standardized. In such a compressor, the leakage in the clearance between the roller and the cylinder chamber is reduced as the cylinder thickness is reduced. At the same time, the sliding loss around the blade is reduced, so that the compression performance is improved.

  However, in this case, a suction passage having a sufficient cross-sectional area cannot be provided on the side surface of the cylinder. [Patent Document 1] discloses a technique in which an intermediate partition plate between a first cylinder and a second cylinder is provided with a branched suction passage communicating with each cylinder chamber.

In particular, in the case of a two-cylinder rotary compressor, if a cylinder that always performs compression and a cylinder that can be switched between compression and stop as needed can be provided, operation according to the load can be performed. Is enlarged and advantageous. The present applicant provides the above-described two-cylinder rotary compressor in [Patent Document 2].
JP-A-9-250477 JP 2004-301114 A

  In the technique of [Patent Document 2], back pressure is applied to the blade on the first cylinder side by a compression spring, and the tip is elastically brought into contact with the circumferential surface of the roller. Therefore, in the first cylinder chamber, the rotating shaft is driven to rotate, and the gas is always compressed and discharged as long as the roller rotates. A pressure (high pressure) in the sealed case is applied as a back pressure to the blade provided in the second cylinder.

  On the other hand, the second cylinder chamber is provided with means for switching and guiding the low pressure gas and the high pressure gas. When the low-pressure gas is guided to the second cylinder chamber, a differential pressure is generated at the blade tip and rear end. The blade tip is pressed and urged to come into sliding contact with the roller peripheral wall, and a normal compression action is performed in this cylinder chamber. A normal operation is performed in which the compression action is performed in the first cylinder chamber and the second cylinder chamber.

  Further, when high pressure gas is introduced into the second cylinder chamber, the front and rear end portions of the blades have the same high pressure atmosphere, and no differential pressure is generated. Since the blade is pushed away by the roller and does not protrude into the cylinder chamber, no compression action is performed. A cylinder resting operation is performed in which the compression action is performed only in the first cylinder chamber.

  As in [Patent Document 1], the cylinder thickness is reduced to reduce the leakage in the clearance between the roller and the cylinder, the sliding loss around the blade is reduced, and the compression performance is improved. If switching between normal operation and idle cylinder operation as in 2] is possible, a two-cylinder rotary compressor having a very high efficiency and a large variable capacity range can be obtained.

  However, as described above, in the technique of [Patent Document 1], a suction passage communicating with the first cylinder chamber and the second cylinder chamber is provided in the intermediate partition plate, and each cylinder chamber is provided in the intermediate partition plate. It is branched to communicate with.

  Thus, the suction passage to each cylinder chamber is provided in common until just before each cylinder chamber, so that the compression operation is interrupted by increasing the pressure of the cylinder side cylinder chamber as shown in [Patent Document 2]. It is difficult to combine the technology to be combined with the technology of [Patent Document 1].

  The present invention has been made on the basis of the above circumstances, and its object is to provide two cylinders, provide a suction passage in an intermediate partition plate interposed between these cylinders, and perform normal operation and idle cylinders. Two-cylinder rotary compressor capable of switching operation, high efficiency, large capacity variable range and improved reliability, and improvement of refrigeration cycle efficiency with this two-cylinder rotary compressor The refrigeration cycle apparatus to be obtained is to be provided.

  In order to satisfy the above object, a two-cylinder rotary compressor of the present invention accommodates an electric motor unit and a compression mechanism unit that are connected to each other through a rotating shaft in a sealed case, and the compression mechanism unit is interposed via an intermediate partition plate. A first cylinder having a first cylinder chamber formed on both end faces and a second cylinder having a second cylinder chamber are provided, and the intermediate partition plate has a main suction passage formed in a radial direction. A first branch suction passage communicating with the first cylinder chamber and a second branch suction passage communicating with the second cylinder chamber are provided from the main suction passage to the first cylinder chamber inside the intermediate partition plate. A first switching position communicating with both the branch suction passage and the second branch suction passage, and a second switching position communicating with either the first branch suction passage or the second branch suction passage from the main suction passage. Switching position With a switchable switching means.

  In order to satisfy the above object, the refrigeration cycle apparatus of the present invention forms a refrigeration cycle with the above-described two-cylinder rotary compressor, a condenser, an expansion mechanism, and an evaporator.

  According to the present invention, the main suction passage is provided in the intermediate partition plate, and the switching between the normal operation and the non-cylinder operation is made possible, the efficiency is increased, the capacity variable range is increased, and the reliability can be improved. A two-cylinder rotary compressor and a refrigeration cycle apparatus that includes this two-cylinder rotary compressor and obtains improved refrigeration cycle efficiency can be provided.

Hereinafter, an embodiment 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. (In order to avoid complications in the drawings, components that are not denoted by reference numerals in the description are not illustrated. Or, although illustrated, they are not denoted in the drawings. same as below)
First, from the configuration of the refrigeration cycle apparatus R, a two-cylinder rotary compressor A, a condenser B, an expansion mechanism 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 the refrigerant on the suction side from the gas-liquid separator E The two-cylinder rotary compressor A is sucked through the pipe Pa.

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 portion 2B is formed 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.

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

  The crankshaft portions c and d are formed with the same amount of eccentricity from each other by the same amount from the central axis of the main shaft portion and the subshaft portion of the rotating shaft 4 with a phase difference of about 180 °. A first roller 13a is fitted to the crankshaft portion c, and a second roller 13b is fitted to the crankshaft portion d. 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 and the intermediate partition plate 7, and the intermediate partition plate 7 and the auxiliary bearing 12, respectively. 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.

FIG. 2 is an exploded perspective view showing the first cylinder 8A and the second cylinder 8B.
The first cylinder 8A is provided with a blade chamber 22a, and the second cylinder 8B is also provided with a blade chamber 22b. The blade chamber 22a includes a blade housing groove 23a that can be slidably moved on both side surfaces of the blade 15a, and a vertical hole portion that is integrally connected to the end portion of the blade housing groove 23a and accommodates the rear end portion of the blade 15a. 24a.

  Further, the first cylinder 8A is provided with a lateral hole 25a communicating the outer peripheral surface and the blade chamber 22a, and the spring member 26 is accommodated therein. The spring member 26 is interposed between the end surface of the rear end of the blade 15a and the inner peripheral surface of the sealing case 1, and applies an elastic force (back pressure) to the blade 15a so that the tip contacts the roller 13a. It is a spring.

  On the other hand, the second cylinder 8B is also provided with a blade chamber 22b. The blade chamber 22b includes a blade storage groove 23b that can be slidably moved on both side surfaces of the blade 15b, and an end portion of the blade storage groove 23b. And a vertical hole portion 24b in which the rear end portion of the blade 15b is accommodated.

  The blade chamber 22b is not provided with a horizontal hole, and therefore, the spring member 26 is not provided as in the blade chamber 22a in the first cylinder 8A. Instead, at least the vertical hole 24 b of the blade chamber 22 b is exposed in the sealed case 1 and is affected by the pressure atmosphere in the sealed case 1.

  That is, the pressure in the sealed case 1 applies a back pressure to the rear end portion of the blade 15b located in the vertical hole portion 24b. As will be described later, since the refrigerant gas compressed by the action of the compression mechanism unit 2 is discharged and filled in the sealed case 1, a high back pressure is applied to the blade 15b of the second cylinder 8B.

  The tip portions of the blades 15a and 15b are formed in a semicircular shape in plan view. The tip of the blade 15a with respect to the first cylinder chamber 14a is always in line contact with the peripheral wall of the cylindrical roller 13a by the action of the spring member 26 regardless of the rotation angle of the roller. The tip of the blade 15b with respect to the second cylinder chamber 14b can make line contact with the peripheral wall of the cylindrical roller 13b regardless of the rotation angle of the roller, if the condition is satisfied.

  When the rollers 13a and 13b are eccentrically rotated along the inner peripheral walls of the cylinder chambers 14a and 14b, the blades 15a and 15b reciprocate along the blade housing grooves 23a and 23b, and the blade rear end is the vertical hole 24a. , 24b.

As shown in FIG. 1 again, the main bearing 11 and the sub-bearing 12 are provided with discharge valve mechanisms, which communicate with the cylinder chambers 14a and 14b, respectively, and are 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.

Next, the intermediate partition plate 7 will be described in detail.
The intermediate partition plate 7 interposed between the first cylinder 8A and the second cylinder 8B is formed to a thickness that is somewhat larger than the thickness of the cylinders 8A and 8B. A main suction passage 30 is provided through the sealed case 1 and extending from the outer peripheral surface of the intermediate partition plate 7 toward the axial direction. A suction refrigerant pipe Pa extending from the gas-liquid separator E is inserted into the main suction passage 30 and is firmly fixed.

  At the tip of the main suction passage 30, there is provided a slider accommodating chamber 31 in which a slider S as switching means described later is accommodated so as to be movable in the front-rear direction of the paper surface. The intermediate partition plate 7 is provided with a first gas outlet 32a that opens from the slider accommodating chamber 31 to the first cylinder 8A.

  The first gas outlet 32a communicates with a notch 33a provided in the inner diameter portion of the first cylinder 8A. The notch 33a is open to the first cylinder chamber 14a and serves as a suction port 33a for the first cylinder chamber 14a.

  Further, the intermediate partition plate 7 is provided with a second gas outlet 32b that opens from the slider accommodating chamber 31 to the second cylinder 8B. The second gas outlet 32b communicates with a notch 33b provided in the inner diameter portion of the second cylinder 8B. The notch 33b opens to the second cylinder chamber 14b and serves as a suction port 33b for the second cylinder chamber 14b.

  In this manner, the suction refrigerant pipe Pa extending from the gas-liquid separator E is inserted and fitted into the main suction passage 30 provided in the intermediate partition plate 7. A first gas outlet 32a provided with a slider accommodating chamber 31 for accommodating the slider S at the tip of the main suction passage 30, and communicating with the suction port 33a of the first cylinder chamber 14a via the slider accommodating chamber 31; A gas outlet port 32b communicating with the suction port 33b of the second cylinder chamber 14b is provided.

  On the other hand, one end portion of the first bypass pipe 35 is connected to a midway portion of the suction refrigerant pipe Pa that connects the gas-liquid separator E and the main suction passage 30 of the intermediate partition plate 7. The first bypass pipe 35 is connected to the first port of the three-way switching valve 36. A second bypass pipe 37 is connected to the second port of the three-way switching valve 36.

  The second bypass pipe 37 penetrates the sealed case 1 and is connected so that the open end faces a slightly upper part of the first cylinder 8A. That is, the second bypass pipe 37 communicates the three-way switching valve 36 and the inside of the sealed case 1. Further, a third bypass pipe 38 is connected to the third port of the three-way switching valve 36.

  The third bypass pipe 38 will be described with reference to FIGS. 3B and 4B. That is, the third bypass pipe 38 penetrates the sealed case 1 and is connected to the boss part 40 provided on the side part of the intermediate partition plate 7. The boss 40 closes one end opening of the slider accommodating chamber 31, and the third bypass pipe 38 communicates with the slider accommodating chamber 31.

Next, the slider S and the slider accommodating chamber 31 for accommodating the slider S will be described in detail.
FIG. 3A is a longitudinal sectional view of a part of the compressor showing the configuration of the slider S and the slider accommodating chamber 31 in a normal operation state. FIG. 3B is a cross-sectional plan view taken along line bb in FIG. FIG. 4A is a longitudinal sectional view of a part of the compressor showing the configuration of the slider S and the slider accommodating chamber 31 in a cylinder resting operation state. FIG. 4B is a cross-sectional plan view taken along line bb in FIG.

In other words, FIGS. 3A and 3B show a state in which the slider S is at the first switching position. 4A and 4B show a state in which the slider S is in the second switching position.
As shown in FIGS. 3 (A) and 4 (A), the slider accommodating chamber 31 for accommodating the slider S has a circular cross section, and its axial direction is as shown in FIGS. 3 (B) and 4 (B). As shown, it is formed in a straight shape with a certain length.

  One end opening portion of the slider accommodating chamber 31 is closed by the boss portion 40, and the third bypass pipe 38 is connected to an attachment hole a provided in the boss portion 40. The end face of the boss 40 protruding into the slider accommodating chamber 31 forms a first positioning step 42. The other end of the slider accommodating chamber 31 does not penetrate the side wall of the intermediate partition plate 7 and is provided partway.

  A hole 43 having a diameter smaller than the diameter of the slider accommodating chamber 31 is provided at the other end of the slider accommodating chamber 31, and one end of the compression spring 44 is inserted therein. A second positioning step 45 is formed on the end surface between the slider accommodating chamber 31 and the hole 43. The end of the compression spring 44 protruding from the hole 43 comes into contact with the end surface of the slider S and elastically presses and urges the slider S.

  The elastic force of the compression spring 44 is sucked into the high pressure and the compressor A when the two-cylinder rotary compressor A is driven as described later and the refrigerant gas is compressed to a predetermined high pressure state. It is smaller than the force due to the pressure difference between the low-pressure refrigerant gas and the low-pressure pressure.

  The cross-sectional shape of the slider S is circular, and its diameter is slightly smaller than the diameter of the slider accommodating chamber 31. The axial length of the slider S is shorter than the axial length of the slider accommodating chamber 31. Accordingly, the slider S can move to the slider accommodating chamber 31 by the difference in the axial length between the slider accommodating chamber 31 and the slider S.

  A guide groove 46 is provided along the axial direction in a part of the peripheral wall of the slider S. A regulating pin 47 is projected from a part of the peripheral wall of the slider accommodating chamber 31 and is inserted into the guide groove 46. For this reason, the slider S is movable along the axial direction with a constant posture without rotating in the circumferential direction.

  In particular, as shown in FIG. 3B, one end surface of the slider S is in close contact with the first positioning step 42 formed on the end surface of the boss 40 in a state where the slider S is in the first switching position. However, the third bypass pipe 38 is connected so that the opening end thereof is in a position where it is further retracted from the end face of the boss portion 40.

  A very small space formed between the opening end of the third bypass pipe 38 and the end face of the boss 40 is referred to as a “first slider back chamber” 50. Further, in this state, a space portion is formed between the other end portion of the slider S and the second positioning step portion 45 by a difference in the axial length between the slider S and the slider accommodating chamber 31. This space portion is referred to as a “second slider back chamber” 51.

  However, as shown in FIG. 4B, when the slider S is in the second switching position, the second positioning step 45 on the circumferential surface of the hole 43 into which the one end of the compression spring 44 is inserted is provided. The other end surface of the slider S is in a close contact state.

  Between the end face of the boss portion 40 and the end face of the slider S, a space chamber corresponding to the difference in axial length between the slider accommodating chamber 31 and the slider S is formed, and this is the first slider back chamber. 50. On the other hand, since the other end surface of the slider S is in close contact with the second positioning step 45, the second slider back chamber 51 has almost no capacity.

  As shown in FIGS. 3B and 4B, the first communication path 53 is provided with a certain length from the end surface of the slider S facing the first positioning step 50. . As shown in FIG. 4A, the first communication path 53 is a cutout portion that is cut into a flat shape at the bottom of the slider S having a circular cross section.

  If the refrigerant gas is led from the third bypass pipe 38 to the first slider back chamber 50 of the slider accommodating chamber 31 and is filled, the refrigerant gas enters the first communication path 53. When the slider S is in the first switching position, the first communication path 53 does not communicate with any part, and therefore the refrigerant gas is filled only without any escape in the first communication path 53.

  On the other hand, if the slider S is in the second switching position, the tip of the first communication path 53 communicates with the second gas outlet 32b provided in the intermediate partition plate 7 in an obliquely downward direction. As described above, since the second gas outlet 32b communicates with the suction port 33b of the second cylinder chamber 14b, the refrigerant gas guided to the third bypass pipe 38 is connected to the first communication passage 53 and the second communication passage 53b. The gas is led to the second cylinder chamber 14b through the gas outlet 32b.

  Further, a horizontal hole is provided in a part of the peripheral surface of the slider S so as to communicate with the main suction passage 30 in a state where the slider S is in the first switching position. An A suction passage 55 is provided that is a hole that branches in an oblique direction and opens to the upper and lower portions of the slider circumferential surface.

  In other words, the A suction passage 55 is provided with a first branch suction passage Aa that is provided obliquely upward from the front end of the lateral hole and opens at the slider peripheral surface. With the slider S in the first switching position, the main suction passage 30 communicates with the suction port 33a of the first cylinder chamber 14a through the first branch suction passage Aa and the first gas outlet 32a.

  Further, the A suction passage 55 includes a second branch suction passage Ab that is provided in an obliquely downward direction from the front end of the lateral hole and opens at the circumferential surface of the slider. With the slider S in the first switching position, the main suction passage 30 communicates with the suction port 33b of the second cylinder chamber 14b through the second branch suction passage Ab and the second gas outlet 32b.

  In the state where the slider S is in the second switching position, a horizontal hole is provided in a part of the peripheral surface of the slider S so as to communicate with the main suction passage 30, and only in an upward oblique direction from the tip of the horizontal hole. A B suction passage 56 is provided which is a hole that is provided and opens at the upper part of the peripheral surface of the slider S.

  That is, the B suction passage 56 communicates with the suction port 33a of the first cylinder chamber 14a from the main suction passage 30 through the first gas outlet port 32a in a state where the slider S is in the second switching position. One branch suction passage Ba is formed.

  Thus, if the slider S is in the first switching position, low-pressure refrigerant gas can be guided from the gas-liquid separator E along the suction refrigerant pipe Pa and the A suction passage 55. The low-pressure refrigerant gas is diverted in the slider S, a part of the refrigerant gas is led from the first branch suction passage Aa to the first cylinder chamber 14a, and the other part is passed from the second branch suction passage Ab to the second cylinder chamber. 14b.

  If the slider S is at the second switching position, low-pressure refrigerant gas can be guided from the gas-liquid separator E along the suction refrigerant pipe Pa and the B suction passage 56. At this time, all of the low-pressure refrigerant gas is led from the first branch suction passage Ba to the first cylinder chamber 14a without being divided in the slider S. Therefore, it is not led to the second cylinder chamber 14b.

  A second communication path 58 formed of a small hole is provided across the central axes of the A suction path 55 and the B suction path 56, which are both side surfaces of the A suction path 55, and the A suction path 55 and the second positioning path A second communication path 58 formed of a small hole is provided across the end surface of the slider S on the side where the step 45 is formed.

  As described above, when the slider S is in the first switching position, the main suction passage 30 to which the suction refrigerant pipe Pa is connected, the first branch suction passage Aa of the A suction passage 55, and the first The outlet 32a and the first cylinder chamber 14a communicate with each other. At the same time, the second branch suction passage Ab of the A suction passage 55 communicates with the second outlet 32b and the second cylinder chamber 14b.

  In this state, the A suction passage 55 communicates with the B suction passage 56 via one second communication passage 58, but the tip of the B suction passage 56 is at a position where it is blocked by the lower surface of the first cylinder 8A. There is no further intrusion from here. Furthermore, since the B suction passage 56 is not in communication with the first communication passage 53 at the bottom of the slider and the first slider back chamber 50 at the end surface of the slider S, the refrigerant gas is introduced first from the B suction passage 56. There is no.

  When the slider S is in the first switching position, the other second communication passage 58 communicates with the second slider back chamber 51, so that it is guided from the main suction passage 30 through the A suction passage 55. The low-pressure refrigerant gas to be filled fills the second slider back chamber 51.

  When the slider S is in the second switching position, as described above, the main suction passage 30, the first branch suction passage Ba of the B suction passage 56, the first outlet 32a and the first cylinder chamber 14a Communicate. The B suction passage 56 communicates with the A suction passage 55 through one second communication passage 58, but the tips of the first and second branch suction passages Aa and Ab are blocked by the lower surface of the first cylinder 8A. And will not invade further.

  Therefore, the low pressure refrigerant gas guided from the A suction passage 55 via the other second communication passage 58 fills the second slider back chamber 51. In any case, regardless of the position of the slider S, the low-pressure refrigerant gas is guided to the second slider back chamber 51 through the main suction passage 30 and the second communication passage 58, and the end of the compression spring 44 is inserted. The hole 43 to be filled is filled.

(1) When normal operation (full capacity operation) is selected:
Normal operation is performed at high loads, such as during startup.
As shown in FIGS. 3A and 3B, the control unit controls the three-way switching valve 36 so that the first port communicates with the third port. And a control part sends an operation signal to the electric motor part 2 via an inverter. The rotating shaft 4 is driven at a high rotation, and the rollers 13a and 13b rotate eccentrically in the cylinder chambers 14a and 14b.

In the first cylinder 8A, since the blade 15a is always elastically pressed and urged by the spring member 26, the tip of the blade 15a is in sliding contact with the peripheral wall of the roller 13a, and the suction chamber enters the first cylinder chamber 14a. And bisect into the compression chamber.
When the inner circumferential surface rolling contact position of the first cylinder chamber 14a of the roller 13a coincides with the blade housing groove 23a, and the blade 15a is most retracted, the space capacity of the first cylinder chamber 14a is maximized.

  Low-pressure refrigerant gas is sucked from the gas-liquid separator 17 into the sealed case 1 of the two-cylinder rotary compressor A through the refrigerant pipe Pa. In other words, the low-pressure refrigerant gas is guided to the slider accommodating chamber 31 via the main suction passage 30 connected to the suction refrigerant pipe Pa, and is switched from the first bypass pipe 35 to the three-way switching by the switching operation on the three-way switching valve 36. It is led to the third bypass pipe 38 via the valve 36.

  In the slider accommodating chamber 31, the first slider back chamber 50 is filled with low-pressure refrigerant gas, and further, the first communication path 53 at the bottom of the slider S is filled. Thus, although a low pressure is applied to one end surface of the slider S, the elastic force of the compression spring 44 that contacts the other end surface of the slider S overcomes and moves the slider S.

  That is, as shown in FIG. 3B, the end surface of the slider S is at the first switching position where it is in close contact with the first positioning step 42. At this time, as shown in FIG. 3A, the main suction passage 30 and the A suction passage 55 are in communication with each other, and low-pressure refrigerant gas is introduced from the gas-liquid separator E through the suction refrigerant pipe Pa.

  The low-pressure refrigerant gas is guided to the first cylinder chamber 14a through the first branch suction passage Aa, the first outlet 32a, and the first suction port 33a. At the same time, the air is guided to the second cylinder chamber 14b via the second branch suction passage Ab, the second outlet 32b, and the second suction port 33b.

As the roller 13a rotates eccentrically, the rolling contact position of the roller 13a with respect to the inner peripheral surface of the first cylinder chamber 14a moves, and the volume of the compression chamber partitioned by the cylinder chamber 14a decreases. Therefore, the gas previously introduced into the cylinder chamber 14a is gradually compressed.
The rotating shaft 4 is continuously rotated, the capacity of the compression chamber in the first cylinder chamber 14a is further reduced, the gas is compressed, and when the pressure rises to a predetermined pressure, the discharge valve mechanism is opened. The high-pressure refrigerant gas is discharged into the sealed case 1 through the valve cover and is filled.

  At least, the inside of the sealed case 1 is in a high-pressure atmosphere due to the compression action in the first cylinder chamber 14a. The blade 15b on the second cylinder 8B side where the rear end portion is exposed in the sealed case 1 has a rear end portion in a high-pressure atmosphere. On the other hand, low pressure refrigerant is sucked into the second cylinder chamber 14b via the main suction passage 30 and the second branch suction passage Ab, and the tip of the blade 15b is in a low pressure atmosphere.

  The front end of the blade 15b is in a low pressure atmosphere and the rear end is in a high pressure atmosphere, and a differential pressure is generated between the front end and the rear end of the blade 15b. The rear end portion of the blade 15b is pushed to a high pressure, and the front end portion comes into contact with the peripheral surface of the roller 13b. The roller 13b in the second cylinder chamber 14b rotates eccentrically with a phase difference of 180 ° from the eccentric rotation of the roller 13a in the first cylinder chamber 14a.

The same compression action is performed in the second cylinder chamber 14b as the blade 15a on the first cylinder chamber 14a side is pressed and urged by the spring member 26 to perform the compression action.
After all, in the two-cylinder rotary compressor A, the compression action is performed in the first cylinder chamber 14a, the compression action is also performed in the second cylinder chamber 14b, and the compression action is performed in both the cylinder chambers 14a and 14b. The normal operation (full capacity operation) is performed.

The high-pressure gas discharged from the sealed case 1 through the refrigerant pipe P is led to the condenser B to be condensed and liquefied, adiabatically expanded by the expansion mechanism C, and the evaporator D takes the latent heat of evaporation from the heat exchange air and cools it. It works. The evaporated refrigerant is guided to the gas-liquid separator E to be gas-liquid separated, and is again sucked into the two-cylinder rotary compressor A from the suction refrigerant pipe Pa.
In the two-cylinder rotary compressor A, the first cylinder chamber 14a and the second cylinder chamber 14b are respectively sucked into the first cylinder chamber 14a and the second cylinder chamber 14b through the main suction passage 30 and the slider S, and circulate through the above-described path. .

(2) When idle cylinder operation (half-capacity operation) is selected:
Although the air conditioning load is large at the time of starting, if the air conditioning operation is continued to some extent, the air conditioning load becomes small. At this time, the idle cylinder operation (operation that halves the compression capacity) is automatically selected.
The control unit controls the three-way switching valve 36 so that the second port and the third port communicate with each other. As shown in FIG. 4B, the high-pressure refrigerant gas in the sealed case 1 is guided to the third bypass pipe 38 via the second bypass pipe 37 and the three-way switching valve 36 and formed in the slider accommodating chamber 31. The first slider back chamber 50 is filled.

  The high-pressure gas that fills the first slider back chamber 50 applies a high pressure that overcomes the elastic force of the compression spring 44 to the end face of the slider 30. The slider S is pushed by the high-pressure gas and slides from the first switching position to the second switching position, and the compression spring 44 contracts.

  As shown in FIG. 4B, the main suction passage 30 is switched from the A suction passage 55 to the B suction passage 56 by the movement of the slider S. The low-pressure refrigerant gas led from the gas-liquid separator E through the suction refrigerant pipe Pa and the main suction passage 30 is led to the first branch suction passage Ba that forms the B suction passage 56.

  Then, the gas is sucked into the first cylinder chamber 14a through the first gas outlet 32a and the suction port 33a. In the first cylinder chamber 14a, the roller 13a rotates eccentrically, and the back end of the blade 15a is constantly subjected to back pressure by the spring member 26. Therefore, the tip of the blade 15a is in sliding contact with the roller 13a and the cylinder chamber 14a. Divide the inside. That is, the compression action is continuously performed in the first cylinder chamber 14a.

  On the other hand, the high-pressure gas filling the first slider back chamber 50 enters the first communication path 53 formed at the bottom of the slider S. Since the slider S is in the second switching position, the first communication path 53 communicates with the second cylinder chamber 14b via the second outlet 32b and the second suction port 33b.

  The second cylinder chamber 14b is filled with high-pressure gas, and the tip of the blade 15b changes to a high-pressure atmosphere. The rear end portion of the blade 15b is exposed to the high-pressure gas in the sealed case 1 and remains in a high-pressure atmosphere.

For the blade 15b, the front end portion is in a high pressure atmosphere, while the rear end portion is in a high pressure atmosphere, and there is no differential pressure at the front rear end portion. For this reason, the blade 15b in the second cylinder chamber 14b is pushed away by the roller 13b, remains stopped at a position away from the outer peripheral surface of the roller 13b, and the compression action in the second cylinder chamber 14b is not performed.
Eventually, only the compression action in the first cylinder chamber 14a is effective, and an operation with half the capacity is performed in response to a small air conditioning load. In addition, you may provide the permanent magnet for hold | maintaining the position of the braid | blade 15b at the time of cylinder resting operation in the braid | blade chamber 22b.

  In the case of a general rotary type rotary compressor, the smaller the cylinder thickness, the smaller the leakage in the clearance between the roller and the cylinder chamber, and the lower the sliding loss around the blade, thereby improving the compression performance. On the other hand, the thickness of the cylinder is reduced, and it is impossible to have a refrigerant suction passage having a sufficient cross-sectional area on the side surface of the cylinder.

  In the present invention, the thickness of the intermediate partition plate 7 is increased so that the cross-sectional area of the main suction passage 30 is sufficiently large. In addition, the suction passages to the first and second cylinder chambers 14a and 14b are common until immediately before, but in the present invention, the intermediate partition plate 7 is provided with the slider S serving as a switching means, so Therefore, a compressor with high efficiency and a large variable capacity range can be obtained.

  The slider S is switched between a first switching position where the first and second cylinder chambers 14a, 14b and the main suction passage 30 are communicated with each other and a second switching position where only the first cylinder chamber 14a is communicated. Therefore, it is possible to switch between normal operation and non-cylinder operation easily and reliably.

  The second cylinder chamber 14b is provided with a roller 13b that rotates eccentrically and a blade 15b that abuts on the peripheral wall of the roller 13b only when a differential pressure is generated between the front end and the rear end due to back pressure. In addition, the slider S is provided with a first communication path 53 that introduces a high pressure into the second cylinder chamber 14b and forcibly holds the tip of the blade 15b away from the roller 13b.

  Therefore, during cylinder resting operation, high pressure can be introduced into the second cylinder chamber 14b, which is the cylinder resting side cylinder chamber, only by moving the slider S, and the blade 15b of the cylinder chamber 14b can be easily held away from the roller 13b. Ensure reliability.

In order to slide the slider S to the first switching position, a low-pressure refrigerant gas is guided to both ends of the slider S to enter a normal operation state, and the slider S is slid to the second switching position at one end of the slider S. The pressure difference of the refrigerant gas was used for the operation of the slider S so that the low-pressure refrigerant gas was introduced and the high-pressure refrigerant gas was introduced to the other end of the slider S to enter the cylinder resting state.
Therefore, the position of the slider S can be switched quickly and the reaction is fast, and the reliability of the operation is ensured.

In the above embodiment, a part of the blade chamber 22b provided in the second cylinder 8B is exposed in the sealed case 1, and the rear end of the blade 15b is exposed to the high-pressure atmosphere in the sealed case 1. Although configured, the present invention is not limited to this.
FIG. 5 is a longitudinal sectional view of a two-cylinder rotary compressor during normal operation in which means for applying back pressure to the blade 15b with respect to the second cylinder chamber 14b is changed, and FIG. 6 similarly applies back pressure to the blade 15b. It is a longitudinal cross-sectional view of the 2-cylinder rotary compressor A at the time of cylinder resting operation in which the means for applying is changed.

  5 and 6, the slider S described above and the slider accommodating chamber 31 for accommodating the slider S are schematically shown, and the three-way switching valve 36 and the first one connected to the three-way switching valve 36 are shown. The third bypass pipes 35, 37, and 38 are omitted. Further, the same parts are denoted by the same reference numerals, and new description is omitted.

  The second blade chamber 22b provided in the second cylinder 8B has an upper surface closed by the intermediate partition plate 7 and a lower surface closed by the auxiliary bearing 12, thereby forming a sealed structure. Similar to the first blade chamber 22a, a lateral hole is provided from the peripheral surface of the second blade chamber 22b, and a plug member to which the first switching pipe 61 is connected after the magnet 60 is fitted therein. It is blocked at 62.

  The magnet 60 is fitted in a horizontal hole, and a groove is provided along the peripheral surface. The left and right side surfaces of the magnet 60 are in communication with each other through the groove. The first switching pipe 61 is connected to the first port of the auxiliary three-way switching valve 63 outside the sealed case 1.

  The second port of the auxiliary three-way switching valve 63 is provided with a second switching pipe 64 connected to the suction refrigerant pipe Pa communicating the gas-liquid separator E and the main suction passage 30. The third port of the auxiliary three-way switching valve 63 is provided with a third switching pipe 65 that faces the open end in the sealed case 1.

  During normal operation, as shown in FIG. 5, the control unit switches and controls the auxiliary three-way switching valve 63 so that the first port communicates with the third port. Accordingly, the high-pressure gas filling the sealed case 1 is guided from the third switching pipe 65 to the first switching pipe 61 via the auxiliary three-way switching valve 63.

The high pressure gas fills the second blade chamber 22b from the end of the first switching pipe 61 through the groove formed in the magnet 60, and further applies a high back pressure to the blade 15b. Therefore, the tip of the blade 15b comes into contact with the circumferential surface of the roller 13b.
As described above with reference to FIG. 3, the slider S is in the first switching position, and the low-pressure refrigerant gas is guided to the second cylinder chamber 14b. Done. The first cylinder chamber is also compressed and enters a normal operating state.

  During the idle cylinder operation, the control unit switches and controls the auxiliary three-way switching valve 63 to communicate the first port and the second port as shown in FIG. Low-pressure refrigerant gas is led from the gas-liquid separator E to the second blade chamber 22b through the second switching pipe 64, the three-way switching valve 63, and the first switching pipe 61.

  While a low back pressure is applied to the rear end portion of the blade 15b, the slider S is in the second switching position as described above with reference to FIG. 4, and the high pressure gas is guided to the second cylinder chamber 14b. Yes. Since the leading end of the blade 15b is in a high-pressure atmosphere, the leading end of the blade 15b is separated from the roller 13b, and the rear end is subjected to differential pressure in the direction in which it is accommodated in the blade chamber 22b.

  When the blade 15b moves and the rear end portion is inserted into the blade chamber 22b, the blade 15b comes into close contact with the magnet 60 and maintains its position. The tip of the blade 15b is separated from the peripheral surface of the roller 13b, and no compression action is performed. A cylinder resting operation state in which the compression action is performed only in the first cylinder chamber 14a.

  When switching from the idle cylinder operation state to the normal operation state, as described above, a high pressure is applied to the rear end portion of the blade 15b, while the slider S moves to the second switching position and enters the second cylinder chamber 14b. Low-pressure refrigerant gas is sucked.

  Therefore, the rear end portion of the blade 15b is quickly and reliably separated from the magnet 60, and the front end portion is slidably contacted with the roller 13b to perform a normal compression action. Even if the configuration shown in FIGS. 5 and 6 is adopted for the blade 15b provided in the second cylinder 8B, the blade 15b operates reliably and maintains reliability.

Although the intermediate partition plate 7 is provided with the slider S in the above-described modified example, the present invention is not limited to this.
For example, as in the prior art disclosed in [Patent Document 1], a first branch suction passage that simply shunts from the main suction passage to the first cylinder chamber 14a and a shunt flow from the main suction passage to the second cylinder chamber 14b. If the magnet 60, the auxiliary three-way switching valve 63, and the switching pipes 61, 64, 65 are combined with the configuration including the second branch suction passage, the switching between the normal operation and the non-cylinder operation can be performed without providing the slider S. Is possible.

  The two-cylinder rotary compressor A described above and the refrigeration cycle apparatus equipped with the compressor A are not limited to the configuration described above, and various modifications can be made within the scope of the present invention. Of course, it is possible.

The longitudinal cross-sectional view and refrigeration cycle block diagram of the 2-cylinder rotary compressor which concern on one embodiment in this invention. The perspective view which decomposed | disassembled the 1st cylinder and 2nd cylinder based on the embodiment. The longitudinal cross-sectional view of the compression mechanism part at the time of a normal driving | operation state based on the embodiment, and the cross-sectional top view which follows a bb line. The longitudinal cross-sectional view of the compression mechanism part at the time of a cylinder resting operation state based on the embodiment, and the cross-sectional top view which follows a bb line. The longitudinal section in the state at the time of normal operation of the 2 cylinder rotary compressor concerning the modification of the embodiment. The longitudinal cross-sectional view in the state at the time of cylinder resting operation of the 2-cylinder rotary compressor which concerns on the modification of 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, 30 ... Main suction passage, Aa, Ba ... First branch suction passage, Ab ... Second branch suction passage, S ... Slider (switching means), 55 ... A suction passage, 56 ... B Suction passage, 13a, 13b ... roller, 15a, 15b ... blade, 53 ... first communication passage, A ... two-cylinder rotary compressor, B ... condenser, C ... expansion mechanism, D ... evaporator.

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 portion is provided with a first cylinder in which a first cylinder chamber is formed and a second cylinder in which a second cylinder chamber is formed on both end faces via an intermediate partition plate,
The intermediate partition plate has a main suction passage formed in the radial direction, and the first branch suction passage communicating with the first cylinder chamber from the main suction passage to the inside of the intermediate partition plate, and the second A second branch suction passage communicating with the cylinder chamber is provided,
A first switching position where the main suction passage communicates with both the first branch suction passage and the second branch suction passage, and any of the first branch suction passage and the second branch suction passage from the main suction passage. A two-cylinder rotary compressor comprising switching means capable of switching to a second switching position communicating with either one of the two. The switching means is provided in the intermediate partition plate, and communicates with only one of the A suction passage communicating with the first cylinder chamber and the second cylinder chamber, and the first cylinder chamber and the second cylinder chamber. And a slider having a B suction passage that is blocked from the other cylinder chamber,
By sliding the slider to the first switching position, the A suction passage communicates with the main suction passage so that the compression operation can be performed in both the first cylinder chamber and the second cylinder chamber. By sliding to the position, the B suction passage communicates with the main suction passage to enable the compression operation in only one of the first cylinder chamber and the second cylinder chamber, and the other cylinder chamber performs compression. 2. The two-cylinder rotary compressor according to claim 1, wherein the cylinder-cylinder operation is performed without performing the operation. The cylinder chamber that performs the cylinder resting operation without the compression operation, the roller that rotates eccentrically, and the tip end portion on the roller peripheral wall only when a differential pressure is generated between the front end portion and the rear end portion due to back pressure. With a blade to abut,
3. The two-cylinder rotary compressor according to claim 2, wherein the slider is provided with a communication path that introduces a high pressure into the cylinder chamber that performs the cylinder resting operation and holds the tip of the blade away from the roller. . In order to slide the slider to the first switching position, working gas suction pressure is applied to both ends of the slider,
To slide the slider to the second switching position, a suction pressure is applied to one end of the slider, and a discharge pressure is applied to the other end of the slider.
4. The two-cylinder rotary compressor according to claim 3, wherein a pressure difference of the working gas is used for the operation of the slider.   A refrigeration cycle apparatus comprising the two-cylinder rotary compressor according to any one of claims 1 to 4, a condenser, an expansion mechanism, and an evaporator.

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