JP2013224595A - Two-cylinder rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a two-cylinder rotary compressor reducing a compressor loss during both of operation at 100% of displacement capacity and operation at a low load, and improving energy saving performance in actual load operation.SOLUTION: A two-cylinder rotary compressor 100 comprises an opening and closing mechanism which is provided in an angular orientation to be a compression chamber side of a first cylinder 11 and a second cylinder 21 during intake bypass operation with intake bypass passages 30, 40 opened and which opens and closes the intake bypass passages 30, 40.

Description

  The present invention relates to a two-cylinder rotary compressor that is a type of refrigerant compressor used in heat pump equipment, and more particularly to a two-cylinder rotary compressor that improves energy saving performance under operating conditions close to actual load.

  Conventionally, a vapor compression refrigeration cycle using a refrigerant compressor is generally used in heat pump equipment such as an air conditioner and a water heater. In other words, heat pump equipment is equipped with a refrigeration cycle formed by connecting refrigerant compressors, condensers, decompression means, and evaporators with pipes, and performs operations according to applications (for example, air conditioning applications and hot water supply applications). It can be done.

  In recent years, as a measure against global warming, energy saving of heat pump equipment has been promoted in various countries by using highly efficient heat pump technology. The energy-saving standards for air conditioners are also being changed to operating standards that are close to actual loads. In Japan, the APF (Full Year Energy Consumption Efficiency) display has been changed since 2011 due to improved efficiency with the conventional cooling / heating average COP. In the future, it is expected to be changed to a new standard close to the actual load. For example, assuming that the rated heating capacity required when starting the air conditioner is 100%, the heating capacity that is always required is about 10% to 50%.

  On-off control has been used for a long time as a means for adjusting the cooling and heating capacity, and there are problems such as large temperature control fluctuation range and vibration noise, and energy saving. In recent years, inverter control for changing the number of revolutions of an electric motor that drives a compressor has become widespread in order to solve this problem. However, in recent years, there is a demand for shortening the start-up time and a demand for operation in a harsher environment (low temperature or high temperature), so a rated capacity of a certain level or more is necessary. The ability required at all times is smaller and the range of abilities that can be driven is expanded. For this reason, the range of the rotational speed of the compressor by the inverter is widened, and the rotational speed range where high efficiency of the compressor is required tends to be widened. In particular, with a low load capacity, it is difficult to maintain the high efficiency of the compressor while continuously operating at a reduced rotational speed.

  Therefore, recently, attention has been paid again to means for mechanically changing the displacement volume of the refrigerant compressor. For example, in a two-cylinder rotary compressor, it is known to improve the compressor efficiency by performing a low-capacity operation by performing a non-compression operation of one compression mechanism at a low load. As such, when the non-compression operation is performed, the pressure in the cylinder chamber is increased and the back pressure chamber on the back of the blade is set at an intermediate pressure, so that the blade is separated from the roller by the pressure difference between the high pressure and the intermediate pressure. A non-compressed operation (cylinderless operation method) is disclosed (for example, see Patent Document 1).

  In addition, it is known that the exclusion volume can be varied by opening and closing a bypass channel (suction bypass system) from the compression chamber to the suction chamber side. As such, in a multi-cylinder rotary compressor having a plurality of cylinders, the high pressure chamber side of one adjacent cylinder and the low pressure chamber side of the other cylinder are provided on an intermediate partition plate located between the cylinders. An open / close mechanism is disclosed that communicates through a short passage, closes the passage during rated operation, and opens the passage to reduce the capacity under low load conditions (for example, Patent Document 2). reference).

JP-A-1-247786 (3rd, 4th pages, etc.) Japanese Patent Publication No. 2-25037 (2nd page, etc.)

  The two-cylinder rotary compressor as described in Patent Document 1 has a low vibration because the torque fluctuation cancels out when the compression process of the two cylinders is shifted by 180 degrees and the maximum torque fluctuation width becomes small at high load. -There is an advantage of a high efficiency twin compressor (2-cylinder rotary compressor), but at low load, only one compression mechanism is compressed (cylinder operation), so low vibration and high efficiency at low speeds. The advantages of a twin compressor (two-cylinder rotary compressor) cannot be obtained. Moreover, the torque fluctuation frequency due to compression is the same as the motor rotation frequency, and the same torque fluctuation characteristic as that of a single compressor is obtained at low load. Therefore, the low speed limit of the compressor rotation speed is at the same level as that of the single compressor, and therefore the effect of expanding the low load capacity range and the improvement of the operation efficiency by the idle cylinder operation are less than expected.

On the other hand, when a suction bypass operation is performed with a two-cylinder rotary compressor as described in Patent Document 2, the advantages of a twin compressor (two-cylinder rotary compressor) with low vibration and high efficiency cannot be obtained. Since the torque fluctuation frequency due to the compression is twice the motor rotation frequency, the low speed limit of the compressor rotation speed can be somewhat wider than that of the single compressor.
Further, in the multi-cylinder rotary compressor as described in Patent Document 2, it is possible to reduce the loss by providing a suction bypass flow path in the intermediate partition plate, but the actual cylinder has a compression (high pressure) chamber. The side and the suction (low pressure) chamber side are arranged on the opposite side by 180 degrees. For this reason, the compression chamber side and the suction chamber side cannot be connected in a short vertical relationship between the two upper and lower cylinders, and the suction bypass flow path becomes a long flow path. In addition, the configuration of the opening / closing mechanism including the operating parts is relatively complicated and large. On the other hand, since the intermediate partition plate of Patent Document 2 is thin, as in Patent Document 1, all of the suction bypass channel and the opening / closing mechanism are accommodated on the inner layer side with the thickness remaining on the surface of the intermediate partition plate. It is difficult to do. That is, even if Patent Documents 1 and 2 are combined, it cannot be said that a practically realizable configuration is shown.

  The present invention solves the problems of the conventional mechanical capacity control type compressor as described above, reduces the compressor loss both during 100% rejection volume operation and during low load operation, and enables actual load operation. An object of the present invention is to provide a two-cylinder rotary compressor with improved energy saving performance.

  A two-cylinder rotary compressor according to the present invention includes two compression elements arranged in parallel in an airtight container with an intermediate partition plate interposed therebetween, an electric motor unit disposed in the airtight container and driving the compression element, A drive shaft that transmits rotational power from the electric motor unit to the compression element, and the compression element includes two cylinders and a long shaft support member that sandwiches one of the cylinders between the intermediate partition plate, A short shaft support member that sandwiches the other of the cylinders with the intermediate partition plate, and formed on both the long shaft support member side and the short shaft support member side, the compression chamber of one cylinder and the other cylinder Two suction bypass passages that communicate with the suction chamber, and an angle direction that becomes the compression chamber side of the cylinder during the suction bypass operation in which the suction bypass passage is opened, open and close the suction bypass passage An opening and closing mechanism, Those were example.

  According to the two-cylinder rotary compressor according to the present invention, the capacity range can be expanded by mechanical capacity control while mechanically ensuring high efficiency of the compressor.

It is a schematic longitudinal cross-sectional view which shows the structure of the 2-cylinder rotary compressor which concerns on Embodiment 1 of this invention, and has shown the state which opened the suction bypass. FIG. 2 is a layout diagram schematically showing the internal configuration of the two-cylinder rotary compressor according to the first embodiment of the present invention in the AA cross section of FIG. 1. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic longitudinal sectional view showing a structure of a two-cylinder rotary compressor according to Embodiment 1 of the present invention, and shows a state where an intake bypass is closed. It is a schematic longitudinal cross-sectional view which shows the structure of the 2-cylinder rotary compressor which concerns on Embodiment 2 of this invention. FIG. 5 is a layout diagram schematically showing the internal configuration of a two-cylinder rotary compressor according to Embodiment 2 of the present invention in the AA cross section of FIG. It is a schematic longitudinal cross-sectional view which shows the structure of the 2-cylinder rotary compressor which concerns on Embodiment 3 of this invention. FIG. 7 is a layout diagram schematically showing an internal configuration of a two-cylinder rotary compressor according to Embodiment 3 of the present invention in the AA cross section of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1.
FIG. 1 is a schematic longitudinal sectional view showing a structure of a two-cylinder rotary compressor 100 according to Embodiment 1 of the present invention, and shows a state where an intake bypass is opened. FIG. 2 is a layout diagram schematically showing the internal configuration of the two-cylinder rotary compressor 100 in the AA cross section of FIG. 1. FIG. 3 is a schematic longitudinal sectional view showing the structure of the two-cylinder rotary compressor 100 according to the first embodiment of the present invention, and shows a state in which the suction bypass is closed. The basic structure and operation of the two-cylinder rotary compressor 100 will be described with reference to FIGS. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The two-cylinder rotary compressor 100 is one of the components of the refrigeration cycle employed in heat pump equipment such as an air conditioner and a hot water heater. The two-cylinder rotary compressor 100 has a function of sucking fluid (for example, refrigerant or heat medium (water, antifreeze liquid, etc.)), compressing it, and discharging it in a high temperature / high pressure state.

<Basic configuration of the two-cylinder rotary compressor 100>
The two-cylinder rotary compressor 100 includes a compression mechanism 99 that drives the first compression element 10 and the second compression element 20 with the drive shaft 6 and an electric motor unit 9 in the internal space 8 a of the sealed container 3. The drive shaft 6 includes a first (short shaft) support member 60, a first cylinder 11 that constitutes the first compression element 10, an intermediate partition plate 5, and a second, from the lower side to the upper side in the axial direction. The second cylinder 21 constituting the compression element 20 and the second (long axis) support member 70 are sequentially stacked, and the compression mechanism 99 is configured in such a state.

  An electric motor unit 9 is attached to the drive shaft 6 above the compression mechanism 99. The drive shaft 6 is rotatably supported by a short shaft portion 6a that is rotatably supported by a first support member 60 that also serves as a bearing portion and a second support member 70 that also serves as a bearing portion, and is connected to the motor portion 9. The long shaft portion 6b, the eccentric pin portion 6c located in the cylinder chamber 12 of the first cylinder 11, the eccentric pin portion 6d located in the cylinder chamber 22 of the second cylinder 21, the eccentric pin portion 6c and the eccentric pin portion 6d. The intermediate shaft portion 6e is connected to the intermediate shaft portion 6e. A rotating piston 13 is attached to the eccentric pin portion 6c. A rotating piston 23 is attached to the eccentric pin portion 6d.

  In the inner space 8 a of the sealed container 3, a lubricating oil storage portion 3 a for lubricating oil that lubricates the compression mechanism 99 is provided on the lowest side in the axial direction of the drive shaft 6. In addition, a compressor discharge pipe 2 is provided above the sealed container 3 so as to communicate with the internal space 8 a of the sealed container 3. Furthermore, the intermediate partition plate 5 is formed so that the compression chamber bypass holes 33 and 43 pass therethrough.

  The 1st compression element 10 and the 2nd compression element 20 are provided with the 1st cylinder 11 and the 2nd cylinder 21 which consist of parallel plates, respectively. In the cylindrical cylinder chambers 12 and 22 of the first cylinder 11 and the second cylinder 21, the rotary pistons 13 and 23 that are eccentrically rotated by the rotation of the drive shaft 6 and the cylinder chambers 12 and 22 are respectively compressed in a high-pressure compression chamber. There are vanes that are divided into 12b and 22b and low-pressure suction chambers 12a and 22a. The vane provided in the cylinder chamber 22 is illustrated as a vane 24 in FIG. The vanes provided in the cylinder chamber 12 are not shown in any of FIGS. 1 to 3, but are provided in the cylinder chamber 12 like the vanes 24.

  Further, the first cylinder 11 and the second cylinder 21 are provided with cylinder suction ports 15 and 25 communicating with the suction muffler 7 and discharge ports 16 and 26 for discharging the compressed refrigerant from the cylinder chambers 12 and 22. . Discharge mufflers 63 and 73 are attached to a first support member 60 and a second support member 70 that also serve as bearings so as to cover the discharge ports 16 and 26.

  The suction muffler 7 includes an inflow pipe 7a into which refrigerant from a refrigerant circuit outside the two-cylinder rotary compressor 100 flows in, a container 7b that communicates with the inflow pipe 7a and stores the refrigerant that has flowed in through the inflow pipe 7a. And an outflow pipe 7c that is provided so as to protrude inside the container 7b and allows the refrigerant stored in the container 7b to flow out to the outside of the container 7b. The outflow pipe 7 c is branched outside the container 7 b and passes through the first cylinder 11 and the second cylinder 21 and communicates with the cylinder suction ports 15 and 25. The outflow pipe 7c is connected to a low pressure introduction pipe 56 to be described later.

<Basic operation of 2-cylinder rotary compressor>
The drive shaft 6 rotates clockwise as viewed from directly above by the electric motor unit 9 (rotation phase θ with reference to the vane position as shown in FIG. 2). As the drive shaft 6 rotates, the eccentric pin portion 6 c and the eccentric pin portion 6 d rotate eccentrically in the cylinder chambers 12 and 22. Accordingly, the rotary pistons 13 and 23 rotate eccentrically, and the low-pressure refrigerant gas sucked from the inflow pipe 7a of the suction muffler 7 passes through the cylinder suction ports 15 and 25, and the suction chamber 12a and the cylinder of the cylinder chamber 12 Inhaled into the suction chamber 22 a of the chamber 22.

  The refrigerant sucked into the suction chambers 12a and 22a is compressed by the rotation of the rotary pistons 13 and 23 in the compression chamber 12b of the cylinder chamber 12 and the compression chamber 22b of the cylinder chamber 22, respectively. When the compressed refrigerant gas reaches a predetermined pressure, the compressed refrigerant gas is discharged from the discharge ports 16 and 26, passes through the discharge mufflers 63 and 73, the internal space 8 a of the sealed container 3, and the clearance between the motor unit 9, and is discharged from the compressor discharge pipe 2. To the condenser side of the refrigerant circuit outside the two-cylinder rotary compressor 100.

<Characteristic configuration of the two-cylinder rotary compressor 100>
The two-cylinder rotary compressor 100 is provided with a first suction bypass passage 30 that allows the compression chamber 22b of the second cylinder 21 and the suction chamber 12b of the first cylinder 11 to communicate with each other. The first suction bypass flow path 30 is formed by attaching the first suction bypass flow path member 31 processed with a flow path groove to the discharge side surface 60 b of the first support member 60. Further, the two-cylinder rotary compressor 100 is provided with a second suction bypass passage 40 that communicates the compression chamber 12b of the first cylinder 11 and the suction chamber 22a of the second cylinder 21. The second suction bypass channel 40 is formed by attaching a second suction bypass channel member 41 having a channel groove processed to the discharge side surface 70 b of the second support member 70.

  In the two-cylinder rotary compressor 100, it is assumed that the excluded volume is reduced from 100% to 50% by opening the first suction bypass passage 30 and the second suction bypass passage 40. The compression chamber bypass holes 33 and 43 formed in the intermediate partition plate 5 and communicating with the first cylinder 11 and the second cylinder 21 have a smaller pressure loss at the time of the suction bypass as the opening diameter is larger.

  When the rotational phase angle θ at which the rotary pistons 13 and 23 are eccentric is 180 degrees, the excluded volume is 50%. Therefore, in the two-cylinder rotary compressor 100, the compression chamber bypass holes 33 and 43 are open when 0 ° <θ <180 °, and the compression chamber bypass holes 33 and 43 rotate when θ> 180 °. The compression chamber bypass holes 33 and 43 are arranged so that the rotation phase angle θ is around 270 degrees so as to be hidden by the pistons 13 and 23 (see FIG. 2).

  In addition, a suction chamber bypass hole (second suction chamber bypass hole) 42 communicating with the second suction bypass channel 40 and a suction chamber bypass hole (first suction chamber bypass) communicating with the first suction bypass channel 30 The rotation phase angle θ is arranged in the vicinity of 90 degrees so as to open and close in conjunction with the opening and closing of the compression chamber bypass holes (first compression chamber bypass holes) 33 and 43 (second compression chamber bypass holes). . This prevents high-pressure oil on the sealing surfaces of the rotary pistons 13 and 23 from flowing into the suction chambers 22a and 12a during the closed rotation phase of the compression chamber bypass holes 33 and 43, causing heating loss and leakage loss. Is the purpose.

  Further, the two-cylinder rotary compressor 100 includes a flow path switching operation unit 50, an operation unit storage chamber 51, a switching back pressure chamber 52, a spring 53, and a high-pressure oil introduction throttle hole 54. At least the flow path switching operation unit 50, the operation unit storage chamber 51, and the switching back pressure chamber 52 correspond to the opening / closing mechanism of the present invention. The switching back pressure chamber 52 communicates with a low pressure introduction pipe 56. The low-pressure introduction pipe 56 is connected to the outflow pipe 7c, and guides low-pressure refrigerant to the switching back pressure chamber 52 by controlling the opening of the valve 55. The low pressure introduction pipe 56 is provided with a valve 55 for opening and closing the flow path.

  The flow path switching operation unit 50 is configured in a cylindrical piston shape, is stored in the operation unit storage chamber 51, and moves up and down according to the pressure state of the switching back pressure chamber 52. The flow path switching operation unit 50 is formed with suction bypass flow path connection grooves 35 and 45. The suction bypass flow path connection grooves 35 and 45 communicate with or not communicate with the first suction bypass flow path 30 and the second suction bypass flow path 40 as the flow path switching operation unit 50 moves up and down. The operation part storage chamber 51 stores the flow path switching operation part 50 so as to be movable up and down. The operating part storage chamber 51 is formed so as to penetrate the intermediate partition plate 5 up and down, and is formed by providing a space portion at a position corresponding to the through part of the intermediate partition plate 5 of the first cylinder 11 and the second cylinder 21. Has been.

  The switching back pressure chamber 52 is formed in the lower part of the working part storage chamber 51 with a diameter smaller than the diameter of the flow path switching working part 50 and becomes a high pressure state or a low pressure state according to the opening and closing of the valve 55. It will become. The spring 53 is provided in the switching back pressure chamber 52 and supports the flow path switching operation unit 50 so as to be movable up and down. The high-pressure oil introduction throttle hole 54 communicates the high-pressure space in the internal space 8 a with the working part storage chamber 51, and guides the high-pressure lubricating oil to the working part storage chamber 51.

<Inhalation bypass open state>
In the open state of the suction bypass shown in FIG. 1, by opening the valve 55, the outflow pipe 7c and the switching back pressure chamber 52 are communicated to bring the switching back pressure chamber 52 into a low pressure state. When the switching back pressure chamber 52 that has been in a high pressure state becomes a low pressure state, a differential pressure is generated, and the piston-shaped flow path switching operation unit 50 is lowered downward in the operation unit storage chamber 51 by the differential pressure. In this way, the suction bypass flow path connection grooves 35 and 45 formed in the flow path switching operation unit 50 are connected to the first suction bypass flow path 30 and the second suction bypass flow path 40, respectively, and the suction chamber bypass hole 42. , 32 communicate with the compression chamber bypass holes 33, 43.

  However, the flow path switching operation unit 50 has a restriction that the first partition 11, the second cylinder 21, and the intermediate partition plate 5 must be within the thickness of the intermediate partition plate 5 by having a structure penetrating in the axial direction. I do not receive it. In addition, by arranging the flow path switching operation unit 50 in the phase on the compression chamber side, the influence of the compression chamber dead volume when operating without suction bypass is reduced. Further, since the high-pressure oil introduction throttle hole 54 has a large resistance, the flow path switching operation unit 50 completely passes through the operation unit storage chamber 51 so that the influence of the pressure of the low-pressure introduction pipe 32 is large when the valve 55 is opened. In this state, the bottom is sealed, and the high pressure oil introduction throttle hole 54 and the switching back pressure chamber 52 are designed not to conduct. Further, in the neutral state, the spring force was adjusted so that the flow path switching operation unit 50 was almost lowered in the operation unit storage chamber 51.

<Inhalation bypass closed state>
In the closed state of the suction bypass shown in FIG. 3, by closing the valve 55, the space under the working part storage chamber 51 including the switching back pressure chamber 52 becomes a high pressure state due to the influence of the high pressure oil introduction throttle hole 54. Then, contrary to when the switching back pressure chamber 52 is in a low pressure state, the flow path switching operation unit 50 is pushed up in the operation unit storage chamber 51. By doing so, the suction bypass flow path connection grooves 35 and 45 formed in the flow path switching operation unit 50 are disconnected from the suction bypass flow paths 30 and 40, respectively.

<Effects of the two-cylinder rotary compressor 100>
As described above, the two-cylinder rotary compressor 100 can perform twin compression operation by opening the valve 55 without lowering the rotational speed of the two-cylinder rotary compressor 100 under a low load condition. In addition, since there is no restriction that the intermediate partition plate 5 is provided with the suction bypass flow path, the flow path cross-sectional area can be increased. Therefore, the pressure loss of the suction bypass passage is relatively small. In addition, a realistic design that can be handled by a conventional processing method is possible. In addition, heating loss, leakage loss, and dead volume loss, which are the problems of the suction bypass, can be designed to be relatively small.

  Therefore, according to the two-cylinder rotary compressor 100, the problems of the conventional mechanical capacity control method are solved, and the compressor loss is reduced both in the operation of 100% excluded volume and in the low load operation, and the compressor efficiency is improved. Thus, the rotational speed range can be expanded by twin compressor operation, and the energy saving performance in actual load operation can be improved.

Embodiment 2. FIG.
FIG. 4 is a schematic longitudinal sectional view showing the structure of a two-cylinder rotary compressor 100A according to Embodiment 2 of the present invention. FIG. 5 is a layout diagram schematically showing the internal configuration of the two-cylinder rotary compressor 100A in the AA cross section of FIG. The two-cylinder rotary compressor 100A will be described based on FIGS. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  The two-cylinder rotary compressor 100A is different from the two-cylinder rotary compressor 100 according to Embodiment 1 in that the flow path switching operation unit 50A is housed inside the intermediate partition plate 5A. Since the basic structure and operation of the two-cylinder rotary compressor 100A are the same as those of the two-cylinder rotary compressor 100 according to Embodiment 1, the description thereof is omitted.

  The flow path switching operation unit 50A is configured in a cylindrical piston shape, is stored in the operation unit storage chamber 51A, and moves in the horizontal direction according to the pressure state of the switching back pressure chamber 52A. Note that the suction bypass flow path connection grooves 35 and 45 are not formed in the flow path switching operation portion 50A. The operating part storage chamber 51A stores the flow path switching operating part 50A so as to be movable in the horizontal direction. The operating part storage chamber 51A is formed as a thin and long cylindrical hole from the outer peripheral side to the inner peripheral side of the intermediate partition plate 5A.

  The switching back pressure chamber 52A is formed at the left end of the working portion storage chamber 51A in the drawing, and becomes a high pressure state or a low pressure state according to the opening and closing of the valve 55. The spring 53A is provided in the switching back pressure chamber 52A and supports the flow path switching operation unit 50A so as to be movable in the horizontal direction. The high-pressure oil introduction throttle hole 54A communicates the high-pressure space of the internal space 8a with the working part storage chamber 51A, and guides the high-pressure lubricating oil to the working part storage chamber 51A.

<Inhalation bypass open state>
FIG. 4 shows that by opening the valve 55, the flow path switching operation unit 50 </ b> A moves in the direction of the drive shaft 6 due to the differential pressure, so that the compression chamber bypass hole 33 of the first cylinder 11 and the suction bypass of the second cylinder 21. The hole 42 communicates with the second suction bypass passage 40, and the compression chamber bypass hole 43 of the second cylinder 21 and the suction bypass hole 32 of the first cylinder 11 pass through the first suction bypass passage 30. And connected to the outflow pipe 7c of the suction muffler 7.

<Inhalation bypass closed state>
On the other hand, when the valve 55 is opened, the operating part storage chamber 51A becomes a low pressure, and the flow path switching operating part 50A moves toward the sealed container 3 due to the differential pressure, so that the compression chamber bypass hole 33, the suction bypass hole 42, the compression The chamber bypass hole 43 and the suction bypass hole 32 can be switched to a closed state where the suction bypass is not communicated.

<Effects of the two-cylinder rotary compressor 100A>
In the two-cylinder rotary compressor 100A, the working part storage chamber 51A is more difficult to process than the working part storage chamber 51 of the two-cylinder rotary compressor 100 according to the first embodiment. The same effect as the cylinder rotary compressor 100 can be obtained.

  Therefore, according to the two-cylinder rotary compressor 100A, the problems of the conventional mechanical capacity control method are solved, and the compressor loss is reduced both in the operation of 100% displacement volume and in the low load operation, and the compressor efficiency is improved. In addition, energy saving performance in actual load operation can be improved, which enables expansion of the rotation speed range by twin compressor operation.

Embodiment 3 FIG.
FIG. 6 is a schematic longitudinal sectional view showing the structure of a two-cylinder rotary compressor 100B according to Embodiment 3 of the present invention. FIG. 7 is a layout diagram schematically showing the internal configuration of the two-cylinder rotary compressor 100B in the AA cross section of FIG. The two-cylinder rotary compressor 100B will be described based on FIGS. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.

  In the two-cylinder rotary compressor 100B, in order to reduce the pressure loss of the suction bypass flow path, absorption chamber bypass holes are provided on both surfaces of the cylinder, and a suction bypass additional flow path member 57 is added inside the intermediate partition plate 5B. The suction chamber bypass hole 32 and the suction chamber bypass hole 42 are different from each other in that they are arranged on both the upper surface side and the lower surface side of the first cylinder 11 and the second cylinder 21, respectively. This is different from the two-cylinder rotary compressor 100 according to the first embodiment and the two-cylinder rotary compressor 100A according to the second embodiment. Since the basic structure and operation of the two-cylinder rotary compressor 100B are the same as those of the two-cylinder rotary compressor 100 according to Embodiment 1, the description thereof is omitted. Further, the point that the flow path switching operation unit 50B is housed inside the intermediate partition plate 5B is the same as that of the two-cylinder rotary compressor 100A according to the second embodiment, and thus the description thereof is omitted.

  The flow path switching operation unit 50B is formed in a cylindrical piston shape, is stored in the operation unit storage chamber 51B, and moves in the horizontal direction according to the pressure state of the switching back pressure chamber 52B. Note that the suction bypass flow path connection grooves 35 and 45 are not formed in the flow path switching operation unit 50B. The operation part storage chamber 51B stores the flow path switching operation part 50B so as to be movable in the horizontal direction. This working part storage chamber 51B is formed as a thin and long cylindrical hole from the outer peripheral side to the inner peripheral side of the intermediate partition plate 5B.

  The switching back pressure chamber 52B is formed at the left end of the working portion storage chamber 51B on the paper surface, and becomes a high pressure state or a low pressure state according to the opening / closing of the valve 55. The spring 53B is provided in the switching back pressure chamber 52B and supports the flow path switching operation unit 50B so as to be movable in the horizontal direction. The high-pressure oil introduction throttle hole 54B communicates the high-pressure space of the internal space 8a with the working part storage chamber 51A, and guides the high-pressure lubricating oil to the working part storage chamber 51A.

  The suction bypass additional flow path member 57 includes a flow path switching operation part, an operation part storage chamber, and a spring. The working part storage chamber constituting the suction bypass additional flow path member 57 is formed at a position facing the working part storage chamber 51B. The flow path switching operation part and the spring constituting the suction bypass additional flow path member 57 are provided at positions facing the flow path switching operation part 50B and the spring 53B in the operation part storage chamber constituting the suction bypass additional flow path member 57. It has been. The flow path switching operation part, the operation part storage chamber, and the spring constituting the suction bypass additional flow path member 57 are configured and function similarly to the flow path switching operation part 50B, the operation part storage room 51B, and the spring 53B.

<Inhalation bypass open state>
In FIG. 6, when the valve 55 is opened, the flow path switching operation unit 50 </ b> B moves in the direction of the drive shaft 6 due to the differential pressure, and the suction bypass of the compression chamber bypass hole 33 of the first cylinder 11 and the second cylinder 21. The hole 42 communicates with the second suction bypass passage 40, and the compression chamber bypass hole 43 of the second cylinder 21 and the suction bypass hole 32 of the first cylinder 11 pass through the first suction bypass passage 30. And connected to the outflow pipe 7c of the suction muffler 7.

<Inhalation bypass closed state>
On the other hand, when the valve 55 is opened, the operating portion storage chamber 51B becomes a low pressure, and the flow path switching operating portion 50B moves toward the sealed container 3 due to the differential pressure, so that the compression chamber bypass hole 33, the suction bypass hole 42, the compression The chamber bypass hole 43 and the suction bypass hole 32 can be switched to a closed state where the suction bypass is not communicated.

<Effects of the two-cylinder rotary compressor 100B>
In the two-cylinder rotary compressor 100B, the working part storage chamber 51B is more difficult to process than the working part storage chamber 51 of the two-cylinder rotary compressor 100 according to the first embodiment. The same effect as the cylinder rotary compressor 100 can be obtained. In addition, the two-cylinder rotary compressor 100B can reduce the pressure loss of the suction bypass passage more than the two-cylinder rotary compressor 100A, and thus a greater improvement effect can be obtained.

  Therefore, according to the two-cylinder rotary compressor 100B, the problems of the conventional mechanical capacity control system are solved, and the compressor loss is reduced both during the operation of 100% excluded volume and during the low load operation, thereby improving the compressor efficiency. In addition, energy saving performance in actual load operation can be improved, which enables expansion of the rotation speed range by twin compressor operation.

  In the above first to third embodiments, the high-pressure hermetic shell type and rotary piston type rotary compression type compressors have been described. However, if the two-cylinder rotary compressor with stacked cylinders is used, other shell types and other compression types are used. Similar effects can be obtained by using similar means in the form. For example, the same effect can be obtained in the case of a semi-sealing type. Alternatively, the same effect can be obtained in the case of the intermediate pressure shell type. The same effect can be obtained for other rotary compression methods (sliding vane method, swing method, etc.).

  2 compressor discharge pipe, 3 sealed container, 3a lubricating oil storage section, 5 intermediate partition plate, 5A intermediate partition plate, 5B intermediate partition plate, 6 drive shaft, 6a short shaft portion, 6b long shaft portion, 6c eccentric pin portion, 6d Eccentric pin part, 6e Intermediate shaft part, 7 Suction muffler, 7a Inflow pipe, 7b Container, 7c Outflow pipe, 8a Inner space, 9 Motor part, 10 First compression element, 11 First cylinder, 12 Cylinder chamber, 12a Suction Chamber, 12b compression chamber, 13 rotary piston, 15 cylinder suction port, 16 discharge port, 20 second compression element, 21 second cylinder, 22 cylinder chamber, 22a suction chamber, 22b compression chamber, 23 rotary piston, 24 vane, 25 Cylinder suction port, 26 discharge port, 30 first suction bypass channel, 31 first suction bypass channel member, 32 suction chamber bypass hole, 33 compression chamber bypass , 35 Suction bypass channel connection groove, 40 Second suction bypass channel, 41 Second suction bypass channel member, 42 Suction chamber bypass hole, 43 Compression chamber bypass hole, 45 Suction bypass channel connection groove, 50 Channel switching Operating section, 50A channel switching operating section, 50B channel switching operating section, 51 operating section storage room, 51A operating section storage room, 51B operating section storage room, 52 switching back pressure chamber, 52A switching back pressure chamber, 52B switching back Pressure chamber, 53 spring, 53A spring, 53B spring, 54 High pressure oil introduction throttle hole, 54A High pressure oil introduction throttle hole, 54B High pressure oil introduction throttle hole, 55 Valve, 56 Low pressure introduction pipe, 57 Suction bypass additional flow path member, 60 First support member, 60b discharge side face, 63 discharge muffler, 70 Second support member, 70b discharge side face, 73 discharge muffler, 99 compression mechanism, 100 2 air Rotary compressor, 100A 2-cylinder rotary compressor, 100B 2-cylinder rotary compressor.

Claims (7)

Two compression elements arranged side by side with an intermediate partition plate in a sealed container;
An electric motor unit disposed in the sealed container and driving the compression element;
A drive shaft for transmitting rotational power from the electric motor unit to the compression element,
The compression element is
Two cylinders,
A long shaft support member sandwiching one of the cylinders with the intermediate partition plate;
A short shaft support member that sandwiches the other of the cylinders with the intermediate partition plate;
Two suction bypass passages formed on both the long shaft support member side and the short shaft support member side, and communicating the compression chamber of one cylinder and the suction chamber of the other cylinder;
A two-cylinder rotary provided with an opening / closing mechanism that is disposed in an angle direction on the compression chamber side of the cylinder during the suction bypass operation in which the suction bypass passage is opened, and opens and closes the suction bypass passage. Compressor. When the rotational phase angle of the two compression elements is shifted by 180 degrees and the rotational phase angle is 180 degrees or more,
A compression chamber bypass hole communicating with the compression chamber of one of the cylinders;
The compression chamber bypass hole and the suction chamber bypass hole are disposed so that the suction chamber bypass hole communicated with the suction chamber of the other cylinder is connected to the suction bypass flow path. The two-cylinder rotary compressor described. The suction chamber bypass hole is arranged at a rotation phase angle of around 90 degrees,
The two-cylinder rotary compressor according to claim 2, wherein the compression chamber bypass hole is disposed in the vicinity of a rotational phase angle of 270 degrees. The opening and closing mechanism is
A flow path switching operation part configured in a piston shape;
An operation section storage section for storing the flow path switching operation section so as to be movable in the vertical direction or the horizontal direction;
A switching back pressure chamber that communicates with the working portion storage portion and drives the flow path switching working portion according to a pressure state;
4. The suction bypass flow path is opened by driving the flow path switching operation unit with the switching back pressure chamber in a low pressure state during the suction bypass operation. 5. The two-cylinder rotary compressor described. The operating part storage part is
The two-cylinder rotary compressor according to claim 4, wherein the two-cylinder rotary compressor is formed so as to penetrate the intermediate partition plate vertically. The operating part storage part is
The two-cylinder rotary compressor according to claim 4, wherein the two-cylinder rotary compressor is formed as a cylindrical hole from an outer peripheral side to an inner peripheral side of the intermediate partition plate. Providing the suction chamber bypass holes on both sides of the cylinder;
The two-cylinder rotary compressor according to claim 6, wherein a suction bypass additional flow path member configured in the same manner as the flow path switching operation section and the operation section storage section is provided in the intermediate partition plate.

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