JP2008057395A - Hermetic rotary compressor and refrigeration cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigeration cycle device capable of increasing a capacity ratio and operating efficiently by providing an outer vessel and making the outer vessel communicate with a compression chamber of one compression mechanism part. <P>SOLUTION: The refrigeration cycle device 1 uses a rotary compressor 100 that includes a first cylinder 131 for performing compression operation and a second cylinder 132 formed capably of change over between compression operation and non-compression operation in the hermetic vessel 102. The device is formed to make the first cylinder chamber 131 communicate to the outer vessel 170 provided outside of the hermetic vessel 102, and to deliver part of compressed refrigerant gas to the outer vessel 170. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a hermetic rotary compressor and refrigeration cycle apparatus used for an air conditioner and the like, and more particularly to a technique capable of increasing efficiency.

  In a refrigeration cycle apparatus such as an air conditioner, for example, a rotary compressor having two compression mechanisms housed in a sealed container is used. Among such rotary compressors, there is one that can vary the compression capacity according to the load. For example, one of the two compression mechanism units is a first compression mechanism unit that always performs a compression operation, and the other is a second compression mechanism unit that can be operated by switching between a compression operation and a non-compression operation. In addition, it is known that the second compression mechanism unit can perform a non-compression operation when the cooling load (or heating load) is small, and an efficient operation can be performed. Moreover, the thing with which the exclusion volume of the compression chamber of a 1st compression mechanism part and a 2nd compression mechanism part differs is known (for example, refer patent document 1).

Further, the cylinder has a cylinder resting control mechanism that opens and closes the suction passage of one of the two compression mechanism sections, and the low pressure of the compression mechanism section is located in the middle of the compression process of the cylinder provided in the other compression mechanism section. There is also known one in which the compression capacity is varied by providing a side and a bypass passage (see, for example, Patent Document 2).
JP 2004-301114 A JP-A-61-4892

  The above-described hermetic rotary compressor has the following problems. That is, if the cylinder displacement volumes of the first compression mechanism unit and the second compression mechanism unit are the same, the capacity ratio (maximum capacity / minimum capacity) is about 2 when the compressor is operated at the commercial power frequency. . If the capacity ratio is small, the operation of the refrigeration cycle apparatus must be adjusted so that, for example, the power supply is frequently turned ON / OFF during the minimum capacity operation (for example, when the room temperature reaches a set temperature). , Driving efficiency decreases.

  In addition, when the displacement volumes of the compression chambers of the two compression mechanism units are different, the compression operation is performed in both compression mechanism units when high output is required at the time of starting or the like. Since the reaction forces are not the same, there is a possibility that imbalance occurs in the motion of the crankshaft that rotates eccentrically, and it cannot be said that the reliability is good. In addition, since the dimensions and the like of the compression chambers are different during full capacity operation, it is difficult to optimize the output efficiency of both compression chambers, and a decrease in COP (coefficient of performance) can be considered.

  Further, a compressor having a cylinder resting control mechanism in one compression mechanism section and having a bypass passage in the cylinder of the other compression mechanism section and the low pressure side of the compression mechanism section sucks hot gas in the compression process into the suction port. Since it is to be returned, the suction gas is recompressed while warming, and the loss increases and the efficiency decreases.

  Therefore, an object of the present invention is to provide a hermetic rotary compressor and a refrigeration cycle apparatus that can be operated with high efficiency by increasing the capacity ratio (maximum capacity / minimum capacity) of the compressor.

  In order to solve the above problems and achieve the object, the hermetic rotary compressor and the refrigeration cycle apparatus of the present invention are configured as follows.

  In a hermetic rotary compressor including a first compression mechanism that performs a compression operation in a sealed container and a second compression mechanism that is configured to be able to switch between a compression operation and a non-compression operation. An external sealed container provided; a communication path that communicates at least the cylinder chamber of the first compression mechanism section during the compression stroke; and the external container; and an on-off valve that is configured to open and close the communication path. It is characterized by being.

  A condenser connected to the hermetic rotary compressor, an expansion device connected to the condenser, and an evaporator connected to the expansion device.

  According to the present invention, high efficiency operation is possible by increasing the capacity ratio of the compressor.

  FIG. 1 is an explanatory diagram showing a configuration of a refrigeration cycle apparatus 1 according to a first embodiment of the present invention and a cross section of a rotary compressor 100 incorporated in the refrigeration cycle apparatus 1, and FIG. Sectional drawing which shows the integrated opening part 134, FIG. 3 is a graph which shows the driving | operation capability by the refrigerating-cycle apparatus 1 of this invention. In FIG. 1, P indicates a branch pipe, K indicates a pressure switching mechanism, and B in FIG. 2 indicates a reference line.

  As shown in FIG. 1, the refrigeration cycle apparatus 1 includes a rotary compressor 100, a condenser 500 connected to the discharge port 101 of the rotary compressor 100, an expansion device 510 connected to the condenser 500, and an expansion device. An evaporator 520 connected to 510 and an accumulator 530 connected to the evaporator 520 are provided.

  The rotary compressor 100 is a two-cylinder rotary compressor, and includes a hermetic container 102, a compression mechanism part 130 provided at the lower part of the hermetic container 102, an electric motor part 150 provided at the upper part of the hermetic container 102, A rotating shaft 160 that connects the compression mechanism unit 130 and the electric motor unit 150 is provided, and an external container 170 that is connected to the compression mechanism unit 130 and is hermetically sealed is provided. The sealed container 102 includes an upper lid 102 a for sealing the sealed container 102.

  The compression mechanism unit 130 includes a first cylinder 131 that forms a first cylinder chamber 131a and a second cylinder chamber 132a that are disposed above and below the rotating shaft 160 via an intermediate partition plate 133. And a cylinder 132. The first and second cylinders 131 and 132 are set to have different outer shape dimensions and the same inner diameter dimension. The outer dimension of the first cylinder 131 is formed slightly larger than the inner diameter dimension of the sealed container 102, and after being press-fitted into the inner peripheral surface of the sealed container 102, the first cylinder 131 is positioned and fixed by welding from the outside of the sealed container 102.

  A main bearing 141 is superimposed on the upper surface of the first cylinder 131, and a first valve cover 142 is provided so as to cover the main bearing 141. The main bearing 141 has a discharge hole 141A for guiding the refrigerant to the valve cover 142. A sub bearing 143 is superimposed on the lower surface of the second cylinder 132, and a second valve cover 144 is provided so as to cover the sub bearing 143. The first valve cover 142, the main bearing 141, the first cylinder 131, the intermediate partition plate 133, the second cylinder 132, the auxiliary bearing 143, and the second valve cover 144 are engaged by a mounting bolt 145 and fixed to the first cylinder 131. The

  Further, the outer dimensions of the intermediate partition plate 133 and the auxiliary bearing 143 are somewhat larger than the inner diameter of the second cylinder 132, and the inner diameter position of the second cylinder 132 is shifted from the center of the second cylinder 132. For this reason, a part of the outer periphery of the second cylinder 132 protrudes in the radial direction from the outer diameters of the intermediate partition plate 133 and the auxiliary bearing 143.

  The intermediate partition plate 133 forms a first cylinder chamber 131a of the first cylinder 131 and a second cylinder chamber 132a of the second cylinder 132, and an eccentric roller 146 described later slides. In addition, an opening 134 provided on the surface of the intermediate partition 133 that is in contact with the first cylinder chamber 131 a and opened and closed by an eccentric roller 146, and the opening 134 communicated with the outside of the sealed container 102 so as to connect to the external container 170. And a communication path 135. A first electromagnetic on-off valve 171 is provided between the communication path 135 and the outer container 170.

  The electric motor unit 150 includes a stator 151 that is fixed to the inner surface of the hermetic container 102, and a rotor 152 that is disposed inside the stator 151 at a predetermined interval and into which the rotating shaft 160 is inserted. I have. The electric motor unit 150 is connected to an inverter 540 that varies the operating frequency, for example, and the inverter 540 is electrically connected to a control unit 550 that controls the inverter 540. In addition, you may operate the electric motor part 150 by connecting with a commercial power source.

  The rotary shaft 160 is pivotally supported by the main bearing 141 and the auxiliary bearing 143 at the midway portion and the lower end portion. Further, the rotary shaft 160 penetrates through the insides of the first and second cylinders 131 and 132, and integrally includes two eccentric portions 161 and 162 formed with a phase difference of about 180 °. The rotation centers of the eccentric parts 161 and 162 are provided on the same straight line, and are assembled so as to be positioned at the inner diameter parts of the first and second cylinders 131 and 132, respectively. Eccentric rollers 146 and 147 that are collinear with each other are accommodated on the peripheral surfaces of the eccentric portions 161 and 162, respectively, so as to be eccentrically rotatable.

  The height dimension of each eccentric roller 146, 147 is formed the same as the height dimension of the first and second cylinder chambers 131a, 132a. Therefore, the eccentric rollers 146 and 147 have a phase difference of about 180 ° from each other. However, the eccentric rollers 146 and 147 are set to the same excluded volume in the cylinder chamber by rotating eccentrically in the first and second cylinder chambers 131a and 132a. The first and second cylinders 131 and 132 are provided with vane chambers 131b and 132b communicating with the first and second cylinder chambers 131a and 132a. The vanes 136 and 137 are accommodated in the respective vane chambers 131b and 132b so as to protrude and retract with respect to the first and second cylinder chambers 131a and 132a.

  Each vane chamber 131b, 132b is integrally connected to each vane storage groove (not shown) in which both side surfaces of each vane 136, 137 are slidably movable, and to the end of each vane storage groove, and the rear ends of the vanes 136, 137 Each vertical hole portion (not shown) in which the portion is accommodated. The first cylinder 131 is provided with a lateral hole that communicates the outer peripheral surface of the first cylinder 131 and the vane chamber 131b, and accommodates the spring member 148. The spring member 148 is interposed between the rear side end surface of the vane 136 and the inner peripheral surface of the sealed container 102, and applies an elastic force (back pressure) to the vane 136 so that the tip edge contacts the eccentric roller 146. It is a compression spring.

  No member other than the vane 137 is accommodated in the vane chamber 132b of the second cylinder 132, but the tip edge of the vane 137 is eccentric roller according to the setting environment of the vane chamber 132b and the action of the pressure switching mechanism K described later. 147 is brought into contact. The front edges of the vanes 136 and 137 are formed in a semicircular shape in plan view, and the vanes 136 and 137 have circular eccentric rollers 146 in plan view regardless of the rotation angle of the eccentric rollers 146 and 147, respectively. Line contact can be made with the 147 peripheral wall.

  When the eccentric rollers 146 and 147 rotate eccentrically along the inner peripheral walls of the cylinder chambers 131a and 132a, the vanes 136 and 137 reciprocate along the vane receiving grooves and the rear end portions of the vanes 136 and 137, respectively. Can move forward and backward from the respective vertical hole portions. As described above, a part of the outer shape of the second cylinder 132 is exposed in the sealed container 102 due to the relationship between the outer dimensions of the second cylinder 132 and the outer dimensions of the intermediate partition plate 133 and the auxiliary receiving shaft 143.

  The portion exposed to the hermetic container 102 is designed to correspond to the vane chamber 132b, and the vane chamber 132b and the rear end of the vane 137 directly receive the pressure in the case. Further, the tip of the vane 136 faces the second cylinder chamber 132a, and the tip of the vane 137 receives the pressure in the cylinder chamber 132a. The vane 137 is configured to move from a higher pressure to a lower pressure in accordance with the magnitude of the pressure received by the front end and the rear end. The first and second cylinders 131 and 132 are provided with mounting holes or screw holes through which the mounting bolts 145 are inserted or screwed, and only the first cylinder 131 is provided with an arc-shaped gas passage hole 138. .

  A discharge pipe 101 is connected to the upper end of the sealed container 102. In addition, suction pipes 560 </ b> A and 560 </ b> B are connected to the bottom of the accumulator 530. One suction pipe 560A penetrates the side of the first cylinder 131 and communicates directly with the first cylinder chamber 131a. The other suction pipe 560B passes through the side of the second cylinder 132 via the sealed container 102 and directly communicates with the second cylinder chamber 132a.

  Further, a branch pipe P is provided which branches from the middle part of the discharge pipe 101 communicating with the sealed container 102 and the condenser 500 and joins the middle part of the suction pipe 560B and is connected to the second cylinder chamber 132a. In the middle of the branch pipe P, a first on-off valve 561 is provided. A second opening / closing valve 562 is provided upstream of the branch portion of the branch pipe P in the suction pipe 560B. The first on-off valve 561 and the second on-off valve 562 are electromagnetic valves, and are configured to be controlled to open and close in response to an electrical signal from the control unit 550.

  In the refrigeration cycle apparatus 1 configured as described above, switching between normal operation (full capacity operation) and one-side cylinder non-compression operation (capacity half operation) is performed as follows. That is, when performing normal operation, the control unit 550 controls the first switching valve 561 of the pressure switching mechanism K to be closed and the second switching valve 562 to be opened. Then, the control unit 550 sends an operation signal to the electric motor unit 150 via the inverter 540. The rotary shaft 160 is driven to rotate, and the eccentric rollers 146 and 147 rotate eccentrically in the first and second cylinder chambers 131a and 132a.

  In the first cylinder 131, the vane 136 is always elastically pressed and biased by the spring member 148, so that the tip edge of the vane 136 is in sliding contact with the circumferential wall of the eccentric roller 146 and the inside of the first cylinder chamber 131 a is compressed with the suction chamber. Divide into rooms. The space capacity of the first cylinder chamber 131a is maximized in a state where the inner roller surface contact position of the first cylinder chamber 131a of the eccentric roller 146 coincides with the vane storage groove and the vane 136 is retracted most. The refrigerant gas is sucked into the upper cylinder chamber 131a from the accumulator 530 through the suction pipe 560A and is filled.

  As the eccentric roller 146 rotates eccentrically, the rolling contact position of the eccentric roller 146 with respect to the inner peripheral surface of the first cylinder chamber 131a moves, and the volume of the compression chamber partitioned by the first cylinder chamber 131a decreases. That is, the gas previously introduced into the first cylinder chamber 131a is gradually compressed. The rotary shaft 160 is continuously rotated, the capacity of the compression chamber of the first cylinder chamber 131a is further reduced, the gas is compressed, and the discharge valve (not shown) is opened when the pressure rises to a predetermined pressure.

  The high-pressure gas is discharged into the sealed container 102 through the valve cover 142 and is filled. And it discharges from the discharge pipe 101 of the airtight container 102 upper part. Similarly to the first cylinder 131, the second cylinder 132 performs a normal compression operation.

  Next, the case where the one-side cylinder non-compression operation is performed will be described. Note that the one-side cylinder non-compression operation is performed only on one side of the second compressor 132 according to the cooling operation or the heating operation, and the other side performs the above-described normal operation. The non-compression operation of the second cylinder 132 is performed as follows. That is, the control unit 550 performs switching setting so that the first on-off valve 561 of the pressure switching mechanism K is opened and the second on-off valve 562 is closed.

  In the first cylinder chamber 131a, the normal compression action is performed as described above, and the high-pressure refrigerant gas discharged into the hermetic container 102 is filled to become a high pressure in the case. A part of the high-pressure refrigerant gas discharged from the discharge pipe 101 is diverted to the branch pipe P and introduced into the second cylinder chamber 132a through the opened first on-off valve 561 and the suction pipe 560B.

  While the second cylinder chamber 132a is in a discharge pressure (high pressure) atmosphere, the vane chamber 132b remains in the same situation as the high pressure in the case. For this reason, the vane 137 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 vane 137 does not move at a position away from the outer peripheral surface of the eccentric roller 147 and maintains a stopped state, and the compression action in the second cylinder chamber 132a is not performed. Eventually, only the compression action in the first cylinder chamber 131a is effective, and an operation with half the capacity is performed.

  Since the inside of the second cylinder chamber 132a is at a high pressure, no refrigerant gas leaks from the sealed container 102 into the second cylinder chamber 132a, and no loss due to the refrigerant gas leak occurs.

  Here, as shown in FIG. 2, the opening 134 is the first when the eccentric roller 146 is rotated clockwise by CW1 with the line connecting the center of the rotating shaft 160 and the center of the vane 136 as the reference line B. Opening of the cylinder chamber 131a is started. Similarly, when the eccentric roller 146 is rotated clockwise by CW2, the opening 134 is closed by the eccentric roller 146 in the first cylinder chamber 131a. When the position of the eccentric roller 146 moves from CW1 to CW2, the opening 134 opens in the first cylinder chamber 131a. When the position of the eccentric roller 146 moves from CW2 to CW1, the opening 134 It is closed by the eccentric roller 146.

  In the normal operation and the one-side cylinder non-compression operation described above, the first electromagnetic on-off valve 171 is closed and each operation is performed. At this time, the refrigerant enters and exits the opening 134 and the communication path 135 up to the first electromagnetic on-off valve 171 and a slight decrease in performance occurs, but the volume of the opening 134 and the communication path 135 is small, Problems such as a reduction in the capacity of the compression mechanism 130 do not occur.

  Next, the release operation (minimum capacity operation) will be described. The release operation is an operation performed when the capacity is further reduced as compared with the above-described one-side cylinder non-compression operation. First, the one-side cylinder non-compression operation described above is performed, and the first electromagnetic on-off valve 171 is opened. When the opening 134 is opened in the compression chamber of the first cylinder chamber 131a by opening the first electromagnetic on-off valve 171, the refrigerant compressed by the rotational compression of the eccentric roller 146 is discharged from the opening 134. It is discharged and moves to the external container 170 via the communication path 135. Further, since the opening 134 is closed by the rotation of the eccentric roller 146, the amount of refrigerant discharged from the discharge hole 141A of the first cylinder chamber 131a is reduced, and the capacity of the compression mechanism unit 130 is higher than that of the one-side cylinder non-compression operation. Further decrease.

  The refrigerant discharged to the outer container 170 through the opening 134 is compressed and thus has a higher temperature and pressure than the refrigerant at the time of suction, but is cooled by the outer container 170 and the communication path 135. The cooled refrigerant returns to the first cylinder chamber 131a due to the pressure difference when the opening 134 is next opened. The release operation is performed by repeating this cycle.

  In this release operation, the capacity reduction rate is desirably 10 to 50%, and this capacity reduction rate can be adjusted by the position of SW2. Further, there is no problem even if the SW1 angle is 0 ° from the reference line B. However, considering the compression efficiency, it is desirable from the viewpoint of the compression efficiency that the eccentric roller 146 is not less than the angle at which the suction hole 560A is closed.

  As described above, according to the refrigeration cycle apparatus 1 according to the present embodiment, as shown in FIG. 3, when the refrigeration capacity during normal operation is 100%, the refrigeration capacity in the one-side cylinder non-compression operation is 50. %, The refrigeration capacity in the release operation is 25 to 45%, and the capacity ratio can be 2.2 to 4.

  As a result, when driven by the inverter 540, it is possible to operate at an efficient high operating frequency, thus enabling highly efficient operation. Moreover, when operating using a commercial power supply, since the frequency of ON / OFF can be reduced, the efficiency of the refrigeration cycle apparatus 1 can be improved.

  FIG. 4 is an explanatory view showing a configuration of a refrigeration cycle apparatus 1A according to the second embodiment of the present invention and a cross section of a rotary compressor 100 incorporated in the refrigeration cycle apparatus 1A. 4 that are the same as those in FIG. 1 are given the same reference numerals, and detailed descriptions thereof are omitted.

  As shown in FIG. 4, the communication path 135 communicated from the opening 134 to the outside of the sealed container 102 is connected at a branch point between the evaporator 520 and the accumulator 530, and between the opening 134 and the branch point. The first electromagnetic on-off valve 171, the release accumulator 170A and the second electromagnetic on-off valve 172 are sequentially provided. Further, the second on-off valve 562 is provided in the middle of the pipe branching from between the first electromagnetic on-off valve 171 and the release accumulator 170A to join the branch pipe P and to the branch pipe P.

  In the refrigeration cycle apparatus 1A thus configured, first, during normal operation, the first on-off valve 561 and the first electromagnetic on-off valve 171 are closed, and the second electromagnetic on-off valve 172 and the second on-off valve 562 are opened. Thus, the operation becomes equivalent to the normal operation of the refrigeration cycle apparatus 1 according to the first embodiment.

  During the one-side cylinder non-compression operation, the first on-off valve 561 is opened, the first electromagnetic on-off valve 171, the second on-off valve 562, and the second electromagnetic on-off valve 172 are closed, and the second cylinder 132 performs the non-compression operation. Thereby, it becomes the operation | movement equivalent to the one-side cylinder non-compression operation of the refrigerating-cycle apparatus 1 which concerns on 1st Embodiment.

  During the release operation, the first on-off valve 561 and the first electromagnetic on-off valve 171 are opened, the second electromagnetic on-off valve 172 and the second on-off valve 562 are closed, and the second cylinder 132 is operated similarly to the one-side cylinder non-compression operation. By performing the non-compression operation, the operation becomes equivalent to the release operation of the refrigeration cycle apparatus 1 according to the first embodiment.

  As described above, the refrigeration cycle apparatus 1A according to the present embodiment has the same effects as those of the refrigeration cycle 1 according to the first embodiment, and further uses both the release accumulator 170A and the external container 170. As a result, the required volume of the accumulator 530 is reduced, so that it is possible to reduce the size even if the second electromagnetic on-off valve 172 needs to be added.

  The present invention is not limited to the above embodiment. For example, in the above-described example, the configuration of the refrigeration cycle apparatus is controlled by a rotary compressor, a condenser, an expansion device, and an accumulator connected to an evaporator. It is applicable even if a four-way valve is provided between the condensers. Further, although the eccentric rollers 146 and 147 are directly provided in the eccentric portions 161 and 162, for example, a rolling bearing may be provided between the eccentric portions 161 and 162 and the eccentric rollers 146 and 147. In addition, various modifications can be made without departing from the scope of the present invention.

Explanatory drawing which shows the cross section of the structure of the refrigerating-cycle apparatus which concerns on the 1st Embodiment of this invention, and the rotary compressor integrated in the refrigerating-cycle apparatus. Sectional drawing which shows the opening part integrated in the same refrigeration cycle apparatus. The graph which shows the driving capability by the same refrigeration cycle apparatus. Explanatory drawing which shows the cross section of the refrigerating-cycle apparatus which concerns on 2nd Embodiment, and the rotary compressor integrated in the refrigerating-cycle apparatus.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Refrigeration cycle apparatus, 100 ... Rotary compressor, 101 ... Discharge port, 102 ... Airtight container, 130 ... Compression mechanism part, 131 ... 1st cylinder, 131a ... 1st cylinder chamber, 132 ... 2nd cylinder, 132a ... 1st 2 cylinder chamber, 133 ... intermediate partition plate, 134 ... opening, 135 ... communication passage, 136,137 ... vane, 138 ... gas passage hole, 141 ... main bearing, 143 ... sub bearing, 144 ... second valve cover DESCRIPTION OF SYMBOLS 146,147 ... Eccentric roller, 148 ... Spring member, 150 ... Electric motor part, 160 ... Rotating shaft, 161, 162 ... Eccentric part, 170 ... External container, 171 ... First electromagnetic on-off valve, 500 ... Condenser, 510 ... Expansion device, 520 ... evaporator, 530 ... accumulator, 540 ... inverter, 550 ... control unit, 560A, 560B ... suction pipe, 561 ... first on-off valve, 562 ... second on-off valve .

Claims (3)

In a hermetic rotary compressor including a first compression mechanism that performs a compression operation in a sealed container, and a second compression mechanism that is configured to be switchable between a compression operation and a non-compression operation.
An external sealed container provided outside the sealed container;
A communication path for communicating the cylinder chamber and the external sealed container at least during the compression stroke of the first compression mechanism section;
A hermetic rotary compressor comprising an on-off valve formed to be able to open and close the communication path.   2. The hermetic rotary compressor according to claim 1, wherein the outer sealed container is an accumulator connected to a suction hole of the second compression mechanism portion. A hermetic rotary compressor according to any one of claims 1 and 2,
A condenser connected to the hermetic rotary compressor;
An expansion device connected to the condenser;
A refrigeration cycle apparatus comprising: an evaporator connected to the expansion device.

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