JP4398321B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus that is, for example, an air conditioner, and more particularly to an improvement of a rotary compressor that constitutes a refrigeration cycle.

For example, in a refrigeration cycle apparatus that is an air conditioner, in particular, a rotary compressor constituting the refrigeration cycle houses an electric motor unit and a compression mechanism unit connected to the electric motor unit in a sealed container, and the compression mechanism unit It is a high-pressure type in the case in which the gas compressed in step 1 is once discharged into a sealed container.
By the way, in recent years, a two-cylinder hermetic rotary compressor provided with two sets of the compression mechanism section above and below is being standardized. If such a compressor can be provided with a compression mechanism part that always performs a compression action and a compression mechanism part that can be switched between compression and stop if necessary, the specifications are expanded and advantageous.
For example, in [Patent Document 1], two cylinder chambers are provided, and if necessary, the back side of one of the blades is set to an intermediate pressure, and high pressure introducing means for introducing a high pressure into the cylinder chamber is provided. A technique is disclosed in which the compression action is interrupted by forcibly holding the blade away from the eccentric roller due to a pressure difference between the front end side and the back side.
JP-A-1-247786

In this type of rotary compressor, it is necessary to provide a check valve for preventing the flow of high-pressure refrigerant from the cylinder chamber to the gas-liquid separator during the capacity reduction operation. The check valve is provided in a refrigerant pipe on the suction side connected to a sealed container constituting the compressor. That is, the check valve is attached outside the hermetic container of the compressor.
Actually, the check valve is connected to the suction side refrigerant pipe by brazing, and the heat at the time of brazing is likely to be transferred to the valve body and the valve seat constituting the check valve. As a result, there is a possibility that the valve body and the valve seat are thermally deformed, and the sealing performance is expected to deteriorate as a check valve.
Furthermore, since the check valve is provided outside the hermetic container constituting the rotary compressor, a space for the check valve arrangement is newly required, leading to an increase in size as a refrigeration cycle apparatus. Furthermore, since the check valve is outside the hermetic container, a collision sound at the time of the check valve operation leaks to the outside of the apparatus, and silent operation is impaired.

  The present invention has been made on the basis of the above circumstances, and the purpose thereof is to provide at least one compression mechanism section for performing a normal operation and a compression operation on the assumption that a plurality of compression mechanism sections are provided. It has pressure switching means that can switch between non-compression operation, and ensures the sealing performance of the check valve mechanism that constitutes the pressure switching means, and further suppresses the enlargement of the device and can achieve quiet operation An object of the present invention is to provide a refrigeration cycle apparatus including a rotary compressor.

In order to satisfy the above-described object, the present invention includes a rotary compressor in which a motor unit and a plurality of compression mechanisms connected to the motor unit are housed in a sealed container, and one compression mechanism of the rotary compressor is provided. Pressure switching means for switching the connection of the refrigeration cycle to the high pressure side or low pressure side of the refrigeration cycle with respect to the cylinder chamber of the part. When the load is large, the low pressure refrigerant is led to the cylinder chamber to perform normal compression operation, and when the load is small In the refrigeration cycle apparatus in which high-pressure refrigerant is introduced into the cylinder chamber to perform non-compression operation, the pressure switching means includes a high-pressure introducing means having an on-off valve in communication with the high-pressure side of the refrigeration cycle and the cylinder chamber, suction passage and the high pressure introducing means formed on one of the compression mechanism portion of the cylinder the guide into the cylinder chamber to the low pressure refrigerant communication between the low pressure side and the cylinder chamber of the cycle The pressure difference between the working chamber connected to the suction passage and the high-pressure refrigerant guided by the high-pressure introduction means when the opening / closing valve of the high-pressure introduction means is movably accommodated in the operation chamber and the suction passage. The valve body which closes a suction passage by this, and the non- return valve mechanism comprised from the valve seat which this valve body contact | abuts .

  According to the present invention, it is possible to secure the sealing performance of the check valve mechanism, suppress the enlargement of the apparatus, and obtain a quiet operation.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional structure of a rotary compressor R and a refrigeration cycle circuit diagram of a refrigeration apparatus provided with the rotary compressor R.
First, the rotary compressor R will be described. 1 is a sealed container, and a lower part in the sealed container 1 is provided with a first compression mechanism part 2A and a second compression mechanism part 2B, which will be described later, and an upper part. Is provided with an electric motor section 3. The electric motor unit 3 and the first and second compression mechanism units 2 </ b> A and 2 </ b> B are connected via the 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 fixed to the inner surface of the hermetic container 1 and a predetermined gap exist inside the stator 5. And a rotor 6 that is disposed on the rotary shaft 4. The electric motor unit 3 is connected to an inverter that varies the operating frequency through an input terminal unit 3a provided at the upper end of the sealed container 1, and a control unit that controls the inverter through the inverter (not shown). Is electrically connected.
Each of the first and second compression mechanism portions 2A and 2B includes a first cylinder 8A and a second cylinder 8B, which are respectively disposed above and below the rotary shaft 4 with an intermediate partition plate 7 interposed therebetween. ing. The first and second cylinders 8A and 8B are set to have different outer shape dimensions and the same inner diameter dimension. The outer diameter of the first cylinder 8A is slightly larger than the inner diameter of the hermetic container 1 and is press-fitted into the inner peripheral surface of the hermetic container 1 and is positioned and fixed by welding from the outside of the hermetic container 1. The

A main bearing 9 is superimposed on the upper surface of the first cylinder 8A, and is fixed to the cylinder 8A via a mounting bolt together with a valve cover. The auxiliary bearing 10 is overlaid on the lower surface portion of the second cylinder 8B, and is fixed to the cylinder 8B via a mounting bolt together with a valve cover.
On the other hand, the rotating shaft 4 is pivotally supported by the main bearing 9 and the auxiliary bearing 10 at the midway portion and the lower end portion. Further, the rotary shaft 4 penetrates through the cylinders 8A and 8B, and integrally includes two eccentric portions 4a and 4b formed with a phase difference of about 180 °. The eccentric portions 4a and 4b have the same diameter as each other, and are assembled so as to be located in the inner diameter portions of the cylinders 8A and 8B. Eccentric rollers 13a and 13b having the same diameter are fitted to the peripheral surfaces of the eccentric parts 4a and 4b.

The first cylinder 8A and the second cylinder 8B have upper and lower surfaces defined by the intermediate partition plate 7, the main bearing 9 and the sub-bearing 10, and cylinder chambers 14a and 14b are formed therein. The cylinder chambers 14a and 14b are formed to have the same diameter and height, and the eccentric rollers 13a and 13b are accommodated in the cylinder chambers 14a and 14b so as to be eccentrically rotatable.
The height of each eccentric roller 13a, 13b is formed substantially the same as the height of each cylinder chamber 14a, 14b. Accordingly, the eccentric rollers 13a and 13b have a phase difference of 180 ° from each other, but are set to the same excluded volume in the cylinder chamber by rotating eccentrically in the cylinder chambers 14a and 14b.
As described above, the first compression mechanism 2A is composed mainly of the first cylinder 8A by the main bearing 9, the intermediate partition plate 7, the first cylinder chamber 14a, and the eccentric roller 13a that rotates eccentrically in the cylinder chamber. Composed. The second compression mechanism 2B is composed mainly of the second cylinder 8B, with the auxiliary bearing 10, the intermediate partition plate 7, the second cylinder chamber 14b, the eccentric roller 13b rotating eccentrically in the cylinder chamber, and the like. The

FIG. 2 is an exploded perspective view showing a part of each of the first compression mechanism 2A and the second compression mechanism 2B.
Each cylinder 8A, 8B is provided with blade chambers 22a, 22b communicating with the cylinder chambers 14a, 14b. Blades 15a and 15b are accommodated in the respective blade chambers 22a and 22b so as to protrude and retract with respect to the cylinder chambers 14a and 14b.
The blade chambers 22a and 22b are integrally connected to the blade housing grooves 23a and 23b in which both side surfaces of the blades 15a and 15b are slidably movable, and the blade housing groove end portions. It consists of the vertical hole parts 24a and 24b accommodated. In particular, the first cylinder 8A is provided with a lateral hole 25 that communicates the outer peripheral surface with the blade chamber 22a, and accommodates the spring member 26 therein. The spring member 26 is interposed between the rear end surface of the blade 15a and the inner peripheral surface of the sealed container 1, and applies an elastic force (back pressure) to the blade 15a so that the tip edge contacts the eccentric roller 13a. It is a compression spring.

The blade chamber 22b on the second cylinder 8B side does not contain any members other than the blade 15b. However, as will be described later, the setting environment of the blade chamber 22b and the operation of the pressure switching mechanism (means) 30 described later. Accordingly, the tip edge of the blade 15b is brought into contact with the eccentric roller 13b.
The leading edges of the blades 15a and 15b are formed in a semicircular shape in plan view, and can make line contact with the circumferential walls of the circular eccentric rollers 13a and 13b in plan view regardless of the rotation angle of the eccentric roller. When the eccentric rollers 13a, 13b are eccentrically rotated along the inner peripheral walls of the cylinder chambers 14a, 14b, the blades 15a, 15b reciprocate along the blade housing grooves 23a, 23b, and the cylinder chambers 14a, 14b are moved to the suction chamber. Partition into compression chambers. The rear end portions of the blades 15a and 15b can be moved forward and backward from the vertical hole portions 24a and 24b.

As described above, a part of the outer shape of the second cylinder 8B is exposed in the sealed container 1 from the relationship between the outer shape of the second cylinder 8B and the outer dimensions of the intermediate partition plate 7 and the auxiliary bearing 10. To do. The portion exposed to the hermetic container 1 is designed to correspond to the blade chamber 22b. Therefore, the blade chamber 22b and the rear end portion of the blade 15b directly receive the pressure in the case.
Since the second cylinder 8B and the blade chamber 22b are structures, there is no effect even if the pressure in the case is applied, but the blade 15b is slidably accommodated in the blade chamber 22b, and the rear end portion is the blade chamber. Since it is located in the vertical hole part 24b of 22b, it receives the pressure in a case directly.

Furthermore, the tip of the blade 15b faces the second cylinder chamber 14b, and the blade tip receives the pressure in the cylinder chamber 14b. Eventually, the blade 15b is configured to move in the direction from the higher pressure to the lower pressure according to the magnitude of the mutual pressure received by the front end and the rear end.
Adjacent to the vertical hole 24b of the blade chamber 22b provided in the second cylinder 8B, and from the differential pressure between the suction pressure guided to the cylinder chamber 14b during normal operation and the internal pressure of the sealed container 1 guided to the blade chamber 22b. A holding mechanism 28 is provided that urges the blade 15b away from the eccentric roller 13a with a small force. The holding mechanism 28 may be a permanent magnet, an electromagnet, or an elastic body such as a spring.

In other words, the holding mechanism 28 pulls the blade 15 away from the eccentric roller 13 with a force smaller than the differential pressure between the suction pressure applied to the second cylinder chamber 14b and the pressure inside the sealed container 1 applied to the blade groove 22. Keep energized. By providing a permanent magnet as the holding mechanism 28, the blade 15 is always magnetically attracted with a predetermined force.
Alternatively, an electromagnet may be provided instead of the permanent magnet, and magnetic attraction may be performed as necessary. Alternatively, the holding mechanism 28 is a tension spring that is an elastic body. One end portion of the tension spring may be hooked on the rear end portion of the blade 15 so that the tension spring is always pulled with a predetermined elastic force.

Each cylinder 8A, 8B is provided with a mounting hole or screw hole into which a mounting bolt for mounting the main bearing 9 or the sub bearing 10 and the valve cover or the like to each cylinder is inserted or screwed. An arc-shaped gas passage hole 27 is provided only in the cylinder 8A.
As shown in FIG. 1 again, the rotary compressor R configured as described above is incorporated in the refrigeration cycle circuit K of the refrigeration cycle apparatus. That is, the discharge refrigerant pipe 18 is connected to the upper end portion of the sealed container 1. The discharged refrigerant pipe 18 is connected to the accumulator 17 via a condenser 19, an expansion mechanism 20 and an evaporator 21.
Suction refrigerant pipes 16a and 16b for sucking and guiding low pressure refrigerant into the rotary compressor R are connected to the bottom of the accumulator 17. One suction refrigerant pipe 16a penetrates the sealed container 1, is connected to a suction hole a provided in the first cylinder 8A, and communicates directly with the first cylinder chamber 14a.

The other suction refrigerant pipe 16b constitutes a suction passage, which will be described later, and passes through the hermetic container 1 and is provided across the second cylinder 8B, the intermediate partition plate 7 and the auxiliary bearing 10, and a check valve mechanism 35. Communicated with Further, the check valve mechanism 35 communicates with a high-pressure introduction passage (high-pressure introduction means) 45 provided to be branched to the refrigeration cycle circuit K.
The suction refrigerant pipe 16b , which is the suction passage, the check valve mechanism 35 and the high pressure introduction passage 45 described later constitute the pressure switching mechanism (pressure switching means) 30.
Explaining from the high-pressure introduction passage 45 first, this one end portion is made up of a branch pipe 46 branched from the middle portion of the discharge refrigerant pipe 18 provided at the upper end portion of the rotary compressor R and extending in the horizontal direction. An electromagnetic opening / closing valve 47 is provided in the middle of the branch pipe 46.

The branch pipe 46 extends vertically downward from the connection part of the electromagnetic on-off valve 47, is bent again in a horizontal direction at a predetermined portion, and passes through the sealed container 1 constituting the rotary compressor R. And, it is connected to a suction hole c provided in the auxiliary bearing 10, and this suction hole c communicates with the check valve mechanism 35.
Next, the check valve mechanism 35 will be described in detail.
The suction refrigerant pipe 16b extending from the accumulator 17 is connected to a suction hole b provided in the intermediate partition plate 7 that passes through the sealed container 1 and is interposed between the first cylinder 8A and the second cylinder 8B. Is done.

FIG. 3A is a cross-sectional view and a bottom view of the intermediate partition plate 7.
The suction hole b provided in the intermediate partition plate 7 and connected to the suction refrigerant pipe 16b is located on the near side of the hole portion 7a through which the rotary shaft 4 is inserted from the outer peripheral surface of the intermediate partition plate 7 toward the central axis direction. Is provided. And the upper valve seat 36 which consists of a hole by which the lower surface side was expanded in the taper shape is provided from the lower surface of the intermediate partition plate 7 to the said suction hole b.
As shown in FIG. 1 again, an operation chamber 37 is provided in a portion of the second cylinder 8B that communicates with the upper valve seat 36 of the intermediate partition plate 7.

FIG. 3B is a plan view and a cross-sectional view of the second cylinder 8B. In particular, the second cylinder 8B is basically the same, although there is a slight difference in shape and configuration from that shown in FIG.
The operation chamber 37 provided in the second cylinder 8B is provided in a portion facing the upper valve seat 36 in the intermediate partition plate 7. The operation chamber 37 includes a guide hole 38 having the same diameter as the enlarged hole diameter of the upper valve seat 36 and penetrating over the upper and lower surfaces of the second cylinder 8B. The guide hole portion 38 is provided with a slight space from the second cylinder chamber 14b formed in the inner diameter portion of the second cylinder 8B, and the wall portion between them leaves the lower half. The upper half is notched. That is, the guide hole portion 38 and the second cylinder chamber 14 b are in communication with each other via the notched weir portion 39.

  As shown in FIG. 1 again, in the auxiliary bearing 10 attached to the lower surface of the second cylinder 8B, the auxiliary bearing 10 has a portion facing the guide hole 38 of the operation chamber 37 provided in the second cylinder chamber 14b. The lower valve seat 40 which is a hole provided at a predetermined depth from the upper surface (that is, does not pass through the auxiliary bearing) is provided.

FIG. 3C is a plan view and a cross-sectional view of the auxiliary bearing 10.
The lower valve seat 40 provided in the auxiliary bearing 10 has the same shape and the same diameter as the upper valve seat 36 provided in the intermediate partition plate 7. Further, a suction hole c is provided so as to communicate with the lower valve seat 40 from the outer peripheral surface of the auxiliary bearing 10. As described above, the branch pipe 46 of the high-pressure introduction passage 45 is connected to the suction hole c.
As shown in FIG. 1 again, in the check valve mechanism 35 configured as described above, a valve body 43 is accommodated in the operation chamber 37. Here, the valve body 43 is spherical and has a diameter slightly smaller than the diameter of the guide hole 38 of the operation chamber 37 and smaller than the plate thickness of the second cylinder 8B. For this reason, the valve body 43 has a margin to freely move in the guide hole 38 of the operation chamber 37.

Moreover, the valve body 43 can be fitted into a tapered hole provided facing the operation chamber 37 in the upper valve seat 36 of the intermediate partition plate 7 and the lower valve seat 40 of the auxiliary bearing 10. The respective valve seats 36 and 40 can be closed in a state.
In this way, the pressure switching mechanism 30 includes the electromagnetic opening / closing valve 47 in the middle, and the high pressure introduction passage 45 provided across the discharge refrigerant pipe 18 and the auxiliary bearing 10, the accumulator 17, and the intermediate partition plate 7. A suction refrigerant pipe 16b which is a suction passage provided over the check valve mechanism 35 provided between the connection end of the high pressure introduction passage 45 and the connection end of the suction refrigerant pipe 16b in the rotary compressor R; Consists of.

Then, the pressure switching mechanism 30 guides the high-pressure refrigerant gas discharged from the compressor R to the second cylinder chamber 14b or passes through the accumulator 17, as will be described later, according to the opening / closing operation of the electromagnetic opening / closing valve 47. The low pressure gas can be guided to the second cylinder chamber 14b.
Next, the operation of the refrigeration cycle apparatus including the rotary compressor R described above will be described.
(1) When normal operation (full capacity operation) is selected:
When normal operation (full capacity operation) is selected, the control unit controls the electromagnetic on-off valve 47 provided in the high-pressure introduction passage 45 to be closed, and the control unit is connected to the inverter circuit of the motor unit 3 via the inverter. Send driving signal. The rotary shaft 4 is rotationally driven, and the first compression mechanism 2A and the second compression mechanism 2B act simultaneously.
That is, the eccentric rollers 13a and 13b rotate eccentrically in the cylinder chambers 14a and 14b. In the first compression mechanism portion 2A, since the blade 15a is always elastically pressed and biased by the spring member 26, the tip edge of the blade 15a is slidably contacted with the peripheral wall of the eccentric roller 13a so as to be in the first cylinder chamber 14a. Is divided into a suction chamber and a compression chamber.

When the position of the inner circumferential surface of the eccentric roller 13a in contact with the blade housing groove 23a coincides with the blade housing groove 23a, the space capacity of the cylinder chamber 14a is maximized. The refrigerant gas is sucked into the first cylinder chamber 14a from the accumulator 17 through the suction refrigerant pipe 16a and is filled.
With the eccentric rotation of the eccentric roller 13a, the rolling contact position of the eccentric roller 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. That is, 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, a discharge valve (not shown) is opened. The high-pressure gas is discharged into the sealed container 1 through the valve cover a and is filled. And it discharges from the discharge refrigerant | coolant pipe | tube 18 of an airtight container upper part.

Since the electromagnetic on-off valve 47 provided in the high-pressure introduction passage 45 is closed, even if the high-pressure gas guided to the discharge refrigerant pipe 18 enters from one end portion of the high-pressure introduction passage 45, it is shut off in the middle. The discharge pressure (high pressure) is not led to the second cylinder chamber 14b which is the end.
On the other hand, the low-pressure evaporative refrigerant evaporated by the evaporator 21 and gas-liquid separated by the accumulator 17 is guided from the suction refrigerant pipe 16b to the check valve mechanism 35 provided in the second compression mechanism portion 2B. Since the high pressure introduction passage 45 is closed, no high pressure is applied to the lower valve seat 40 provided in the auxiliary bearing 10.
As shown in FIG. 4A, only the low-pressure refrigerant is guided to the operation chamber 37 provided in the second cylinder 8B via the suction refrigerant pipe 16b, and the valve accommodated in this operation chamber. The body 43 is pushed by the low-pressure refrigerant and rests on the lower valve seat 40 of the auxiliary bearing 10 to close it.

Therefore, a low-pressure refrigerant is introduced from the accumulator 17 into the second cylinder chamber 14 b through the guide hole portion 38 and the weir portion 39 that constitute the operation chamber 37. Therefore, the second cylinder chamber 14b is in a suction pressure (low pressure) atmosphere, while the blade chamber 22b is exposed in the sealed container 1 and is under a discharge pressure (high pressure). In the blade 15b, the front end portion is under a low pressure condition and the rear end portion is under a high pressure condition, and there is a differential pressure at the front and rear end portions.
Due to the effect of this differential pressure, the tip of the blade 15b is pressed and urged so as to be in sliding contact with the eccentric roller 13b. That is, 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. Eventually, in the rotary compressor R, a full capacity operation is performed in which the compression action is performed by both the first compression mechanism portion 2A and the second compression mechanism portion 2B.
The high-pressure gas discharged from the sealed container 1 through the discharge refrigerant pipe 18 is led to the condenser 19 to be condensed and liquefied, adiabatically expanded by the expansion mechanism 20, and the evaporator 21 takes away the latent heat of evaporation from the heat exchange air. Makes a cooling effect. Then, the evaporated refrigerant is guided to the accumulator 17 and separated into gas and liquid, and again sucked into the first and second compression mechanism portions 2A and 2B of the compressor R from the suction refrigerant tubes 16a and 16b. Cycle through the path.

(2) When special operation (half-capacity operation) is selected:
When a special operation (capability half operation) is selected, the control unit switches and sets the electromagnetic on-off valve 47 provided in the high-pressure introduction passage 45 to be opened. In the first compression mechanism portion 2A, the normal compression action is performed as described above, and the high-pressure gas discharged into the sealed container 1 is filled to become a high pressure in the case.
The high-pressure gas filling the hermetic container 1 is discharged from the discharge refrigerant pipe 18, but a part of the high-pressure gas is diverted from the discharge refrigerant pipe to the branch pipe 46 and led to the high-pressure introduction passage 45 and opened. It is introduced into the check valve mechanism 35 in the compressor R through the electromagnetic on-off valve 47.

As shown in FIG. 4B, the high-pressure refrigerant gas guided from the branch pipe 46 connected to the sub-bearing 10 blows up the valve body 43 that has closed the lower valve seat 40, and the intermediate partition plate 7. The upper valve seat 36 provided in is closed. When the valve body 43 closes the upper valve seat 36, the lower valve seat 40 is opened. For this reason, the high-pressure refrigerant gas is guided to the check valve mechanism 35 through the high-pressure introduction passage 45 and further fills the second cylinder chamber 14b.
Thus, while the second cylinder chamber 14b is in the discharge pressure (high pressure) atmosphere, the blade chamber 22b remains in the same situation as the high pressure in the case. Therefore, the blade 15b is affected by the high pressure at both the front and rear ends, and there is no differential pressure at the front and rear ends.

The blade 15b maintains a stopped state without moving at a position separated from the outer peripheral surface of the eccentric roller 13b, and the second cylinder chamber 14b is not compressed and the second compression mechanism 2B is in a stopped state. Eventually, only the compression action in the first compression mechanism portion 2A is effective, and an operation with half the capacity is performed.
A part of the high-pressure gas filling the second cylinder chamber 14b tends to flow backward from the suction refrigerant pipe 16b to the accumulator 17. However, the valve body 43 in the operation chamber 37 closes the upper valve seat 36 and prevents the backflow from the suction refrigerant pipe 16b side serving as the suction passage to the accumulator 17. Further, since the inside of the second cylinder chamber 14b is at a high pressure, no leakage of compressed gas from the sealed container 1 into the second cylinder chamber 14b occurs, and no loss is caused thereby. Therefore, it is possible to operate with half the capacity without lowering the compression efficiency.

Unlike a conventional compressor, a complicated mechanism for fixing the blade to one compression mechanism at the top dead center is not required, and a spring member for biasing the blade can be omitted. In addition, the pressure switching mechanism 30 can be configured by providing the check valve mechanism 35 at the connection portion between the high pressure introduction passage 45 provided with the electromagnetic on-off valve 47 in the middle and the suction refrigerant pipe 16b communicating with the accumulator 17. A variable structure is possible with a simple structure, which is advantageous in terms of cost, is excellent in manufacturability, and can provide a highly efficient rotary compressor.
In particular, the check valve mechanism 35 is provided inside the sealed container 1 constituting the rotary compressor R, so that the switching sound does not leak to the outside and the operation is quiet and the appearance is simplified and the productivity is improved. Can be obtained. Furthermore, the increase in the size of the apparatus is suppressed, contributing to cost reduction.

The check valve mechanism 35 includes an upper valve seat 36 and a lower valve seat 40 with respect to the valve body 43. That is, the valve body 43 sets the operation direction to the vertical direction, and closes the lower valve seat 40 (opens the upper valve seat 36 from the state where the upper valve seat 36 is closed (lower valve seat 40 is opened)). When shifting to the state of opening, the valve body 43 can be easily and reliably closed by its own weight.
FIG. 5 shows a modification of the first embodiment.
Since only the shape structure of the valve body 43A constituting the check valve mechanism 35 and the upper and lower valve seats 36A and 40A opened and closed by the valve body is different, all other structures are the same. The same number is attached and a new description is omitted.

Here, the valve body 43A has a tapered upper end portion and a simple cylindrical lower end portion. The diameter of the valve body 43A is slightly smaller than the diameter of the operation chamber 37, and the height dimension of the valve body is formed smaller than the height dimension of the operation chamber. Therefore, the valve body 43A can move freely in the up and down direction in the operation chamber 37, as described above.
The upper valve seat 36A that is opened and closed by the valve body 43A is provided in the intermediate partition plate 7, and the lower valve seat 40A is provided in the same portion of the auxiliary bearing 10. Needless to say, the upper valve seat 36A and the lower valve seat 40A have a shape structure that is reliably opened and closed by the valve body 43A.

In any of the valve bodies 43 and 43A, a material having higher hardness than a material constituting the upper and lower valve seats 36 and 40 is selected as the material constituting the valve bodies. As a result, the familiarity of the valve seat with respect to the valve body can be improved, high sealing performance can be secured as a check valve, and the backflow of high-pressure compressed gas can be reliably prevented to prevent performance degradation. .
FIG. 6 shows another modification of the first embodiment.
6A, 6B and 6C are sectional views of the intermediate partition plate 7 and an upper valve seat 36B which will be described later, a sectional view of the state in which the upper valve seat 36B is attached to the intermediate partition plate 7, and It is a bottom view of the intermediate partition plate 7 in a state.

That is, the upper valve seats 36 and 36A described above are formed by directly drilling the intermediate partition plate 7. Here, the intermediate partition plate 7 only needs to be processed by a simple hole 36C, and separately prepared. The valve seat 36B is fitted and fixed in the hole 36C. Further, although not specifically shown, the lower valve seat in the sub-bearing 10 may be similarly fitted and fixed to a separate valve seat.
This separate valve seat 36B uses a material different from the parts forming the suction passage (in the present embodiment, the intermediate partition plate 7), for example, a non-ferrous metal material such as brass or copper, or a synthetic resin material. I will do it. With such a valve seat 36B, the familiarity with the valve bodies 43, 43A can be improved, and a check valve mechanism 35 having high sealing performance can be obtained, and the backflow of high-pressure compressed gas can be ensured. To improve performance.

FIG. 7 is a configuration diagram of a refrigeration cycle circuit including the rotary compressor according to the second embodiment. Here, since the other components are the same except for a check valve mechanism and a pressure switching mechanism including a high-pressure introduction passage, which will be described later, the same reference numerals are given and a new description is omitted.
One end of the suction refrigerant pipe 16 a extending from the bottom of the accumulator 17 passes through the sealed container 1 and is connected to a suction hole d provided in the main bearing 9. The other suction refrigerant pipe 16b communicates with the second cylinder chamber 14b through a suction hole e provided in the second cylinder 8B.

One end of the high-pressure introduction passage 45 is connected to the discharge refrigerant pipe 18 and is composed of a branch pipe 46 provided with an electromagnetic on-off valve 47 in the middle. However, the other end of the branch pipe 46 is connected to a suction hole f provided in the intermediate partition plate 7.
A lower valve seat 40 is provided in the suction hole f of the intermediate partition plate 7, and an upper valve seat 36 is provided in the suction hole d of the main bearing 9. An operation chamber 37 is provided in the first cylinder 8 </ b> A interposed between the main bearing 9 and the intermediate partition plate 7. The upper part of the operation chamber 37 faces the upper valve seat 36, and the lower part of the operation chamber 37 faces the lower valve seat 40. A valve body 43 is slidably accommodated in the operation chamber 37, and the upper and lower valve seats 36 and 40 can be opened and closed with respect to each other according to the degree of pressure applied to the operation chamber 37.

That is, in the first embodiment, the pressure is switched for the second cylinder chamber 14b, but in the second embodiment, the pressure is switched for the first cylinder chamber 14a. The first compression mechanism 2A is provided with a check valve mechanism 35.
Since the operation in the first compression mechanism portion 2A and the second compression mechanism portion 2B is substantially the same as the operation opposite to that of the first embodiment described above, Detailed explanation is omitted.
The branch pipe 46 may be directly connected to the sealed container 1. The present invention can also be applied to a device provided with three or more compression mechanisms.

The longitudinal cross-sectional view and refrigeration cycle block diagram of the rotary compressor which concern on the 1st Embodiment of this invention. The perspective view which decomposed | disassembled each part of the 1st compression mechanism part and 2nd compression mechanism part based on the embodiment. Sectional drawing and bottom view of an intermediate partition plate according to the same embodiment, a plan view and a sectional view of a second cylinder, a plan view and a sectional view of a secondary bearing. The figure explaining the mutually different effect | action of a non-return valve mechanism based on the embodiment. The figure explaining the structure of the different valve body in the non-return valve mechanism based on the modification of the embodiment. The figure explaining the attachment of the valve seat of another piece with respect to the intermediate partition plate based on the further different modification of the embodiment. The longitudinal cross-sectional view and refrigeration cycle block diagram of the rotary compressor based on the 2nd Embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Sealed container, 3 ... Electric motor part, 2A ... 1st compression mechanism part, 2B ... 2nd compression mechanism part, R ... Rotary type compressor, 14a ... 1st cylinder chamber, 14b ... 2nd cylinder chamber 30 ... Pressure switching mechanism (pressure switching means), 47 ... Electromagnetic switching valve, 45 ... High pressure introduction passage (high pressure introduction means), 16b ... Suction refrigerant pipe (suction passage), 36 ... Upper valve seat, 40 ... Lower valve seat 43 ... Valve body, 35 ... Check valve mechanism.

Claims (3)

In the sealed container, provided with a rotary compressor formed by housing an electric motor part and a plurality of compression mechanism parts connected to the electric motor part,
For the cylinder chamber of one compression mechanism of this rotary compressor, it has a pressure switching means for switching the connection to the high pressure side or the low pressure side of the refrigeration cycle,
When the load is large, low pressure refrigerant is introduced into the cylinder chamber to perform normal compression operation,
When the load is small, in the refrigeration cycle apparatus for guiding the high-pressure refrigerant to the cylinder chamber and performing the non-compression operation,
The pressure switching means is
A high-pressure introducing means that communicates the high-pressure side of the refrigeration cycle with the cylinder chamber, and has an on-off valve in the middle;
A suction passage that communicates the low pressure side of the refrigeration cycle with the cylinder chamber and guides the low pressure refrigerant to the cylinder chamber;
An operating chamber formed in the cylinder of the one compression mechanism section , connected to the high pressure introducing means and the suction passage; and movably accommodated in the operating chamber; and when the on / off valve of the high pressure introducing means is opened A valve body that closes the suction passage by a pressure difference between the high-pressure refrigerant guided by the high-pressure introduction means and the low-pressure refrigerant guided to the suction passage, and a check valve mechanism that includes a valve seat that contacts the valve body. A refrigeration cycle apparatus characterized by.   2. The refrigeration according to claim 1, wherein a valve body constituting the check valve mechanism has a spherical or conical shape and is formed of a material having a hardness higher than that of the valve seat constituting the check valve mechanism. Cycle equipment.   2. The valve seat according to claim 1, wherein the valve seat is formed separately from each other using a material different from a material forming the suction passage of the one compression mechanism, and is attached to the suction passage. Item 3. The refrigeration cycle apparatus according to any one of Items 2 to 3.

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