JPS6149584B2 - - Google Patents

Description

[Detailed description of the invention]

The present invention relates to a refrigeration system, and more particularly, to a refrigeration system that is equipped with a capacity control mechanism that controls the capacity of a compressor and that is capable of performing refrigeration operation at a capacity that corresponds to a refrigeration load. In general, a capacity control mechanism for a compressor includes a bypass port provided between the suction port and the discharge port in the cylinder of the compressor, and a bypass pipe disposed outside the frame of the compressor in the bypass port. One end of the bypass pipe is connected, and the other end of the bypass pipe is connected to a suction passage communicating with the suction port, and a solenoid valve is interposed in the middle of the bypass pipe. Open the solenoid valve,
the bypass port is opened to the inlet port side,
The effective volume of the cylinder can be reduced, or when the load is large, that is, at full load, the solenoid valve can be closed, the bypass port can be closed, and the effective volume of the cylinder can be increased. It controls the capacity of However, according to the above structure, the bypass pipe is disposed outside the frame of the compressor, so if the diameter of the bypass pipe is increased, the radius of curvature of the curved portion required for the pipe also increases. Therefore, the routing dimensions of the bypass pipe when piping become larger, and the solenoid valve used for the bypass pipe also becomes larger.As a result, a large space is required around the compressor, and the entire device becomes larger. However, there was a problem of high costs. Furthermore, due to the above-mentioned constraints, if the diameter of the bypass pipe is made smaller, the flow path resistance will increase, and during capacity control operation in which capacity control is performed by opening the solenoid valve,
The problem arises that the pressure drop of the refrigerant passing through the bypass pipe and the solenoid valve becomes large, resulting in large energy loss and a decrease in the effective energy ratio (hereinafter referred to as EER). Moreover, according to the capacity control mechanism having the above structure, the bypass pipe is connected between the bypass port and the suction port side, in other words, it is not connected between the high pressure discharge port side. Even if the solenoid valve is opened when the compressor is stopped, it is not possible to equalize the high and low pressures to reduce the load when the compressor is started, and capacity control is only performed by opening and closing the solenoid valve. Therefore, only two-step control can be performed. As described above, in order to solve the problem of the capacity control mechanism using a bypass pipe disposed outside the frame of the compressor, it is conceivable to form a bypass passage within the frame of the compressor. In this case, the desired cross-sectional area of the passage can be obtained without taking up any special space for the bypass, so the problems of the above-mentioned increase in size and reduction in EER can be solved, but on the other hand, the bypass , to be formed within the structure;
When adjusting the bypass amount, the frame itself must be changed, and as a result, changing the control width becomes complicated. It is necessary to prepare a compressor, which is disadvantageous not only in terms of manufacturing but also in terms of management. Furthermore, even if the bypass passage is formed within the compressor structure, it is not possible to equalize the pressure when the compressor is stopped, and it is not possible to perform capacity control in two or more stages. Even if a bypass path is formed within the frame, the above-mentioned problem of the mechanism for arranging the bypass pipe outside the frame cannot be fundamentally solved. The present invention solves the problems of the external bypass and internal bypass by organically combining a bypass pipe provided outside the frame of the compressor (external bypass) and a bypass path provided within the framework (internal bypass). The main purpose is to be able to control the capacity without reducing the EER, increasing the size or increasing the cost, and to easily control the amount of bypass during capacity control. The object of the present invention is to provide a refrigeration system that can adjust the bypass amount, increase the lower limit of the control width of capacity control, and even perform pressure equalization when the operation is stopped. The object of the present invention is to provide a refrigeration system that can be used over a long period of time and that can also perform pressure equalization when the operation is stopped. Therefore, the first claim set forth in claim 1
In the second invention (specific invention), in the frame of the compressor 1, one end is connected to the suction port 1a of the cylinder 16 and the discharge port 1a of the cylinder 16.
a first bypass passage 50 that opens into the cylinder chamber 16a at an intermediate portion between the cylinder b and the other end that communicates with the suction port 1a;
The first bypass passage 50 is provided with an on-off valve 70 for opening and closing the first bypass passage 50, and a tubular body is disposed outside the frame of the compressor 1, and one end of the tubular body is connected to a low pressure. side and the other end communicates with the high pressure side to form a second bypass passage 60, and an intermediate position 64 of the second bypass passage 60 communicates with the back chamber 71 of the on-off valve 70, while the other end communicates with the high pressure side. A solenoid valve 80 is interposed between the intermediate position 64 and the low pressure side of the second bypass path 60, and a capillary reach tube 90 is interposed between the intermediate position 64 and the high pressure side. The compressor 1 is characterized in that the capacity of the compressor 1 is controlled by opening and closing the first bypass passage. The bypass path increases the lower limit of the control width of the bypass amount during capacity control and also makes it possible to equalize the pressure.Furthermore, by selecting the capillary installed in the second bypass path, the bypass flow during capacity control is increased. The amount, ie, the control width, can also be changed easily. Further, the second invention as set forth in claim 4 is such that the specific invention described above is connected to a four-way switching valve on the inlet/outlet side of the compressor, and by switching the four-way switching valve 23, the refrigerant is This is applied to a refrigeration system that allows heating and cooling by reversing the flow direction. Further, the third invention described in claim 6 is the second invention in the above-mentioned specific invention.
Two first and second solenoid valves and a capillary reach tube (hereinafter abbreviated as capillary) are installed in the bypass path.
By controlling the opening and closing of the two first and second solenoid valves, full load operation with zero bypass amount, partial load operation where capacity is controlled only with the first bypass path, and first and second solenoid valves are incorporated. The fourth invention described in claim 9 is capable of performing three-step controlled operation including partial load operation in which capacity is controlled using two bypass paths. This is applied to a refrigeration system in which a four-way switching valve is connected to the inlet/outlet side of the compressor, and by switching the four-way switching valve, the flow direction of the refrigerant is reversible to enable heating and cooling. In addition, a fifth invention described in claim 11 is a modification of the specific invention described above, in which a four-way switching valve is connected to the inlet/outlet side of the compressor, and by switching the four-way switching valve, the refrigerant is Applicable to a refrigeration system capable of cooling and heating by reversing the flow direction, the second bypass path includes two first and second solenoid valves, two first and second capillaries, and these two capillaries are arranged in parallel. Incorporating two check valves provided in
By controlling the opening and closing of the two first and second solenoid valves, there are three stages: full load operation where the bypass amount is zero, and partial load operation where the capacity is controlled using the first and second bypass paths. In addition, when the two solenoid valves are both opened during cooling, partial load operation can be performed by using the first and second bypass paths together. Further, a sixth invention as set forth in claim 13 is the above-mentioned specific invention, wherein the second bypass path includes two first and second capillaries and two first and second solenoid valves. and by controlling the opening and closing of the first and second solenoid valves by incorporating the second capillary and the second solenoid valve in parallel,
Full load operation with a bypass amount of zero, partial load operation where capacity is controlled by a second bypass path using only the first capillary, and capacity controlled by a second bypass path using the first and second capillaries. This allows for controlled operation over three stages of partial load operation. First, an embodiment of the specific invention will be described based on FIGS. 1 to 3. As schematically shown in FIG. 1, the refrigeration system of the present invention basically includes a compressor 1, a condenser 2, an expansion mechanism 3, and an evaporator 4, and controls the capacity of the compressor 1. It incorporates a capacity control mechanism 5,
A suction passage 6 communicating with the suction port 1a of the compressor 1
is connected to the evaporator 4, and the discharge passage 7 communicating with the discharge port 1b of the compressor 1 is connected to the condenser 2, and the compressor 1 is operated. A refrigeration cycle shown by the arrow is formed, and cooling is performed by the evaporation action in the evaporator 4. As shown in FIGS. 2 and 3, the compressor 1 includes a closed casing 10, a motor 11, and a compression mechanism 1.
The compression mechanism 12 includes an upper frame 14, a lower frame 15, a cylinder 16 interposed between these frames 14 and 15, and a cylinder of the cylinder 16. Room 1
6a and a rotor 17 having vanes 18 incorporated therein, and this rotor 17 is coupled to the shaft 13. The upper frame 14 has one end communicating with the suction port 1a, and the other end communicating with the suction passage 6.
The cylinder 16 is provided with a suction passage 19 that communicates with the cylinder chamber 16a.
A discharge passage 20 is provided which has a discharge port 1b opening into the casing 10 at the other end and opening into the casing 10. Next, the capacity control mechanism 5 incorporated in the refrigeration system configured as described above will be explained. This capacity control mechanism 5 constitutes a main part of the present invention, and basically, one end opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end is the inlet port 1
A, a first bypass passage 50 communicating with a, and a second bypass passage 60 having one end communicating with the low pressure side communicating with the suction port 1a and the other end communicating with the high pressure side communicating with the discharge port 1b, Said first bypass path 5
0 is provided with an on-off valve 70 for opening and closing the bypass passage 50, and a back chamber 71 of this on-off valve 70 is provided with an on-off valve 70 for opening and closing the bypass passage 50.
An intermediate position 64 of the second bypass passage 60 is communicated, and a solenoid valve 80 is provided between the intermediate position 64 and the second bypass passage 60 located on the low pressure side.
Further, a capillary 90 is interposed between the intermediate position 64 and the second bypass path 60 located on the high pressure side, and the capacity of the compressor 1 is controlled by opening and closing the electromagnetic valve 80. It is. As shown in FIGS. 2 and 3, the first bypass passage 50 is provided in the lower frame 15 of the compressor 1, and one end thereof is connected to the cylinder chamber 16a.
A valve chamber 51 is vertically formed below the opening, and extends horizontally from the side of the valve chamber 51. is communicated with the suction port 1a via the suction port 1a and a through hole 16b formed in the cylinder 16, and the second
The bypass passage 60 is formed by a tubular body disposed outside the frame, and this second bypass passage 60 mainly connects the tubular body to the outside of the casing 10 of the compressor 1, as shown in FIG. one end of which is connected to the suction passage 6 or the upper frame 1.
On the low pressure side of the suction passage 19 formed in 4,
The other end is connected to the discharge passage 7 or the cylinder 16.
It is connected to the high pressure side of the discharge passage 20 formed in the. Further, an on-off valve 70 for opening and closing the first bypass passage 50 is installed inside the valve chamber 51, and is made of a metal poppet valve, and is erected from a plug 72 screwed into the lower opening of the valve chamber 51. Setup guide 73
The on-off valve 70 is supported so as to be freely slidable in the vertical direction.
A spring 74 is placed above the flange formed at the bottom of the
is provided and is always biased in the opening direction by the spring 74, and a sealing material 75 is provided on the lower surface of the flange.
The rear chamber 71 is formed between the lower surface of the sealing material 75 and the upper surface of the plug 72. Further, an intermediate position 64 of the second bypass path 60
is communicated with the back chamber 71 mainly by:
As shown in FIGS. 1 and 2, a branch point 61 is connected to an intermediate position 64 of the tubular body forming the second bypass path 60, and the upper frame 1 of the compressor 1
4. Connecting path 6 to cylinder 16 and lower frame 15
2, the lower end of this communication path 62 communicates with the back chamber 71, and the upper end communicates with the upper frame 14.
The branch pipe 61 is connected to the opening to the outside through a connecting pipe 63, and the solenoid valve 8 interposed in the second bypass passage 60 is connected to the branch pipe 61 through the connecting pipe 63.
0, a part of the discharged gas is transferred to the capillary 90, the branch pipe 61 and the communication path 62.
The discharge gas is introduced into the back chamber 71 through the opening/closing valve 7.
0 is closed. In FIGS. 2 and 3, 21 is a suction valve, and 22 is a discharge valve. Therefore, in the above configuration, when performing refrigeration operation, the capacity of the compressor 1 is controlled by opening and closing the solenoid valve 80 according to the cooling load, and when the cooling load is large, the capacity of the compressor 1 is controlled. teeth,
The electromagnetic valve 80 is closed to perform full load operation, and when the cooling load is small, the electromagnetic valve 80 is opened to perform partial load operation. That is, when the electromagnetic valve 80 is closed, a portion of the discharged gas on the high pressure side flows from the second bypass path 60 connected to the high pressure side to the on-off valve 70 via the branch pipe 61 and the communication path 62 as described above. Since the pressure of the discharged gas acts on the on-off valve 70 without being affected by the capillary 90, the on-off valve 70 moves upward against the spring 74. Then, the first bypass path 50 is closed. Therefore, the compressor 1 performs a compression operation with a capacity corresponding to the total volume of the cylinder chamber 16a. When the electromagnetic valve 80 is opened from this state, the second bypass passage 60 is opened from the high pressure side to the low pressure side, so that the high pressure discharge gas introduced from the high pressure side is reduced in pressure by the capillary 90. , the gas flows to the low pressure side at a lower pressure than the high pressure discharge gas. As a result, the pressure acting on the back chamber 71 of the on-off valve 70 is also reduced, and the on-off valve 70 is opened by the action of the spring 74, and the first bypass path 50 is opened. Therefore, no compression is performed between the suction port 1a of the compressor 1 and the opening position of the first bypass passage 50, and the volume of the cylinder chamber 16a is reduced. By opening the second bypass passage 60, a part of the discharged gas bypasses to the low pressure side and performs capacity control, so this capacity control is added to the capacity control due to opening of the first bypass passage 50, and the total control width is can be made larger. Furthermore, when the drive of the compressor 1 that performs capacity control as described above is stopped and the operation is stopped, at the same time, by opening the solenoid valve 80, the pressure between high and low pressures is equalized by the second bypass path 60. This can reduce the load when restarting. When the operation is stopped, the opening of the second bypass passage 60 also opens the on-off valve 70, so when restarting, the above-mentioned partial load operation is necessarily performed, and the starting load can be further reduced. be. As described above, when controlling the capacity of the compressor 1, the capacity control by the first bypass path 50 and the capacity control by the second bypass path 60 are used together, and the total control width of both bypass paths 50 and 60 is determined. Therefore, the lower limit of the control width can be increased, and
Even if the diameter of the tubular body forming the second bypass path 60 is made smaller, the cross-sectional area of the first bypass path 50 can be increased, so the pressure drop during capacity control can be reduced compared to the overall ratio. , the drop in EER can also be reduced. Furthermore, the second bypass path 60 is formed of a tubular body and is disposed outside the frame of the compressor 1, and the capillary 90 is interposed in the second bypass path 60. Even if the capacity control width is constant, the overall control width can be easily changed by selecting the capillary 90, and by using compressors 1 of the same capacity, refrigeration systems with different control widths can be obtained for each product. Furthermore, when the operation is stopped, the electromagnetic valve 80 can be opened to open the second bypass passage 60, so the second bypass passage 60 can be used as a pressure equalization circuit between high and low pressures. In the embodiment described above, if the solenoid valve 80 is closed when energized and opened when not energized,
When the refrigeration operation is stopped, the solenoid valve 80 is always opened without being operated, and the pressure can be equalized between high and low pressures. In comparison, pressure equalization compensation is possible with energy savings. Next, a second embodiment of the invention will be described based on FIG. 4. FIG. 4 shows an application of the specific invention to a heat pump type refrigeration system, in which standard operation can be adjusted according to cooling and heating. As is well known, heat pump refrigeration equipment is
As shown in the figure, a four-way switching valve 23, an expansion mechanism 25 for cooling, an expansion mechanism 24 for heating, and check valves 26 and 27 provided in parallel with these expansion mechanisms 24 and 25 are used to control the four-way switching valve 23. By switching, the flow direction of the refrigerant is made reversible as shown by the solid line and dotted line in FIG. 4, thereby forming a cooling refrigeration cycle shown by the dotted line in FIG. 4 and a heating refrigeration cycle shown by the solid line in FIG. 4. In order to apply this refrigeration system, the tubular body forming the second bypass path 60 may be connected to the low pressure side and the high pressure side as in the embodiment described above, but preferably, the tubular body forming the second bypass path 60 may be connected to the low pressure side and the high pressure side. One end of the body is connected to a first gas pipe 28 which has a high pressure during cooling and a low pressure during heating, and the other end is connected to a second gas pipe 29 which has a low pressure during cooling and a high pressure during heating. The second bypass passage 60 is formed between the two gas pipes 28 and 29, and the intermediate position 64 of the second bypass passage 60 and the first
The electromagnetic valve 80 is connected between the connection position to the gas pipe 28
Also, the intermediate position 64 and the second gas pipe 2
The capillary 90 is interposed between the connection position and the connection position to the capillary 9. In the above configuration, when the electromagnetic valve 80 is closed during cooling, the back chamber 71 of the on-off valve 70 communicates with the second gas pipe 29 through which low-pressure gas flows via the second bypass path 60. Therefore, the pressure in the back chamber 71 becomes lower than the pressure of the low pressure gas due to the action of the capillary 90, and the on-off valve 70 opens. Therefore, the first bypass path 50 is opened, and operation can be performed with the capacity controlled only by this first bypass path 50. Furthermore, when the solenoid valve 80 is closed during heating,
The back chamber 71 of the on-off valve 70 is connected to a second gas pipe 2 through which high-pressure gas flows via the second bypass path 60.
9, the pressure in the back chamber 71 becomes the pressure of the high pressure gas, and the on-off valve 70 is closed. Therefore, the first and second bypass paths 50, 6
Full load operation with zero closed is possible. It is possible to open the electromagnetic valve 80 during cooling and heating as described above, and when it is opened during cooling, the second bypass passage 60 is opened, and by opening the second bypass passage 60, the opening/closing valve 70 is opened. Since the back chamber 71 of the back chamber 71 directly communicates with the first gas pipe 28 through which high-pressure gas flows without going through the capillary 90, the pressure becomes high, the on-off valve 70 is closed, the first bypass path 50 is closed, and the second bypass path 50 is closed. Capacity control operation is performed using only the passage 60, and is used for rapid cooling pulldown. Also, when opened during heating, the second
The bypass passage 60 is opened, and this opening causes the back chamber 71 of the on-off valve 70 to directly communicate with the first gas pipe 28 through which low-pressure gas flows, so that the back chamber 71 has a low pressure, and the on-off valve 70 The first bypass passage 50 is also opened, and capacity control operation is performed by jointly using the first and second bypass passages 50 and 60, which is used for intermediate periods and weak heating. As described above, during cooling when the load is lower than during heating, capacity control operation can be performed in which only the first bypass path 50 or only the second bypass path 60 is opened, and during heating, the capacity control operation can be performed in which only the first bypass path 50 or the second bypass path 60 is opened. Full load operation with the two bypass paths 50 and 60 closed, and the first
Capacity control operation with the second bypass paths 50 and 60 open can be performed, and the standard rated operation during cooling/heating can be changed, making it possible to perform cooling/heating operation with high EER. Next, a third embodiment of the invention will be described based on FIG. 5. The difference between this invention and the above-mentioned specific invention (see FIG. 1) is that two solenoid valves are provided in the second bypass passage 60, and by opening and closing these solenoid valves, capacity control can be performed in three stages. This is what we did. 5 schematically shows the refrigerant piping system as in FIG. 1, and the same reference numerals are used for the same components as in FIG. 1. In FIG. 5, reference numeral 81 is a solenoid valve having the same function as the solenoid valve 80 shown in the embodiment of the specific invention described above, but the reference numeral is changed for convenience of explanation.
This solenoid valve 81 is referred to as a first solenoid valve, and a solenoid valve provided separately from this first solenoid valve 81 is referred to as a second solenoid valve and is designated by the reference numeral 82. 5 shows an intermediate position 6 of the second bypass path 60 to the rear chamber 71.
4 and the high pressure side, the capillary 90 and the second solenoid valve 82 are interposed. In this configuration, when the first solenoid valve 81 is closed and the second solenoid valve 82 is opened, both the first and second bypass paths 50 and 60 are closed, allowing full load operation, and the first solenoid valve 82 is closed. When the valve 81 is opened and the second solenoid valve 82 is closed, the back chamber 71 is communicated with the low pressure side, so only the first bypass passage 50 is opened, and partial load capacity control is performed only by this first bypass passage 50. When the operation is completed and the first and second solenoid valves 81 and 82 are opened, the first and second solenoid valves 81 and 82 are opened.
The bypass paths 50 and 60 are both open, and partial load capacity control operation can be performed by these bypass paths 50 and 60. Partial load capacity control operation is divided into two stages, including full load operation and three stages.
Step-by-step controlled operation becomes possible. Next, a fourth embodiment will be explained based on FIG. 6. FIG. 6 shows that the specific invention described above is applied to a heat pump type refrigeration system, and two solenoid valves are installed in the second bypass path 60, and capacity control can be performed in three stages by opening and closing these solenoid valves. 4, one end of the tubular body forming the second bypass path 60 is connected to the first gas pipe 28, which has a high pressure during cooling and a low pressure during heating, as in the embodiment shown in FIG.
The other end is connected to a second gas pipe 29 which has a low pressure during cooling and a high pressure during heating, thereby forming the second bypass path 60 between the first and second gas pipes 28 and 29. . An intermediate position 64 of the second bypass path 60 to the back chamber 71 and the first gas pipe 28
The first electromagnetic valve 81 is interposed between the intermediate position 64 and the connection position to the second gas pipe 29, and the second electromagnetic valve 81 is interposed between the intermediate position 64 and the connection position to the second gas pipe 29.
1. A capillary 90 is inserted. Thus, in the above configuration, by opening and closing the first and second solenoid valves 81 and 82, capacity control can be performed in three stages as shown in the following table. In the table, the first and second valves are the first and second valves, respectively.
The solenoid valve is a second solenoid valve, and the first and second paths are the first and second solenoid valves.
This refers to a bypass road and a second bypass road.

[Table] As is clear from the above table, the partial load operation in the third stage during cooling is performed with the first bypass path 50 closed and only the second bypass path 60 open. Next, a fifth embodiment of the invention will be described based on FIG. 7. FIG. 7 shows that the specific invention is applied to a heat pump type refrigeration system, and the second bypass path 60 is
In addition to the capillary provided on the side connected to the gas pipe 29, a capillary is also provided on the side connected to the first gas pipe 28,
From the middle position 64 of the second bypass path 60 to each of the gas pipes 2
Check valves 100, 10 that allow flow only to 8, 29
1 in parallel, the capacity control of the third stage during cooling can be performed by jointly using the first and second bypass paths 50 and 60. In this embodiment, a capillary provided between the intermediate position 64 and the connection position to the first gas pipe 28 is referred to as a first capillary and has a reference number 91, and a capillary between the intermediate position 64 and the second The capillary provided between the connecting position and the gas pipe 29 is referred to as a second capillary, and its reference number is 92. Therefore, these first and second capillaries 9
The reason why the check valves 100 and 101 are provided in parallel with the capillaries 91 and 92 is to prevent one capillary 91 or 92 from acting in response to changes in the flow direction of the gas refrigerant flowing into the second bypass path 60 during heating and cooling. This is for the purpose of Note that 102 and 103 are the respective capillaries 91,
These check valves 102 and 103 are not particularly necessary. Finally, a sixth embodiment of the invention will be described based on FIG. 8. The difference between this invention and the above-mentioned specific invention is that two solenoid valves and two capillaries are provided in the second bypass path 60, and by opening and closing these solenoid valves, the capillary is used to control the compressor 1. The advantage is that the capacity can be controlled in three stages. In other words, in the second invention shown in FIG. 5, in addition to the capillary 90, another capillary 94
is provided in parallel with the second solenoid valve 82. What is shown in FIG. 8 is a schematic representation of the refrigerant piping system, similar to FIGS. 1 and 5, and parts having the same configuration as those in FIGS. 1 and 5 are
The same symbols are used. In addition, in FIG. 8, 93 is the same as the capillary 90 in the specific invention and the second invention described above, but for convenience of explanation, the symbol is changed,
The capillary 94 provided separately is called the third capillary and the fourth capillary. 8, the fourth capillary 94 is arranged in parallel with the second electromagnetic valve 82 on the high pressure side with respect to the position where the second bypass passage 60 communicates with the back chamber 71. It was established. In this configuration, when the first solenoid valve 81 is closed, the back chamber 71 of the on-off valve 70 communicates with the high pressure side and becomes high pressure regardless of whether the second solenoid valve 82 is opened or closed. 70 is closed, the first and second bypass paths 50 and 60 are both closed,
Full load operation is possible. Further, when the first solenoid valve 81 is opened, the second solenoid valve 81 is opened.
Regardless of whether the solenoid valve 82 is opened or closed, the on-off valve 7
Since the back chamber 71 of No. 0 communicates with the low pressure side and has a low pressure, the on-off valve 70 is opened and both the first and second bypass paths 50 and 60 are opened. At this time,
When the second electromagnetic valve 82 is closed, the fourth capillary 94 is activated, and the gas refrigerant bypassing from the high pressure side passes through the two third and fourth capillaries 93 and 94 and bypasses to the low pressure side. On the other hand, when the second solenoid valve 82 is opened, the gas refrigerant bypassing from the high pressure side does not pass through the fourth capillary 94, but passes through the second solenoid valve 82 with less resistance, and is depressurized only in the third capillary 93. bypassed to the low pressure side. Therefore, when the second electromagnetic valve 82 is opened or closed, the passage resistance of the second bypass path 60 changes, and the amount of bypass is adjusted in accordance with this change, and the amount of bypass is adjusted according to this change. Road 50,60
Partial-load operation that performs capacity control can be adjusted to two stages by using this in combination, and three-stage controlled operation is possible in addition to full-load operation. In the above embodiment, the fourth capillary 94 was connected in parallel with the second solenoid valve 82, but
In addition, the third capillary 93 and the second solenoid valve 8
It may be connected in parallel in a series circuit with 2. As described above, since the present invention (specific invention) uses the two first and second bypass paths together, it is possible to increase the lower limit of the control width when performing capacity control, and the second bypass path is connected to the compressor. A capillary is interposed in the tubular body, and the bypass amount of the second bypass path can be set by the capillary, and by adjusting the bypass amount, the first and second bypass paths can be set. Since the total control width by the second bypass path can be changed and the capillary can be easily replaced, the control width during the capacity control can be easily changed. Furthermore, even if the diameter of the tubular body forming the second bypass path is reduced, the pressure drop during capacity control can be reduced, and the drop in EER can also be reduced. In addition to having the function of a bypass path, since it is an operation circuit for the first bypass path, a special operation circuit and a control valve such as a three-way valve for controlling the opening and closing of the first bypass path can be eliminated. Moreover, since the second bypass path is provided between the high and low pressures, it also serves as a pressure equalization circuit that equalizes the pressure between the high and low pressures when the operation is stopped, and the load at the time of startup can be reduced. Moreover, according to the second invention, the same effects as those of the above-mentioned specific invention can be achieved with respect to a refrigeration system capable of heating and cooling. Further, according to the third invention, the capacity can be controlled in three stages while obtaining the same effects as the above-mentioned specific invention. Furthermore, according to the fourth invention, the same effects as those of the above-mentioned specific invention can be achieved in a refrigeration device capable of heating and cooling, and moreover, the capacity can be controlled in three stages. Further, according to the fifth invention, it is possible to achieve the same effect as the above-mentioned specific invention with respect to a refrigeration device capable of heating and cooling, and moreover, the capacity can be controlled in three stages, Particularly, when both electromagnetic valves are opened during cooling, partial load operation can be performed using the two bypass paths in combination. Further, according to the sixth invention, while obtaining the same effect as the above-mentioned specific invention, capacity control can be controlled in three stages, and partial load operation can be performed.
It is possible to switch between using only the first capillary and using both capillaries.

[Brief explanation of the drawing]

Fig. 1 is a refrigerant piping system diagram showing one embodiment of the specified invention, Fig. 2 is an enlarged longitudinal cross-sectional view of only the compressor, and Fig. 3 is an enlarged cross-sectional view of the compressor including the refrigerant piping system. , Fig. 4 is a refrigerant piping system diagram showing an embodiment of the second invention, Fig. 5 is a refrigerant piping system diagram showing an embodiment of the third invention, and Fig. 6 is a refrigerant piping system diagram showing an embodiment of the third invention. Refrigerant piping system diagram showing an example of
The figure is a refrigerant piping system diagram showing a fifth embodiment.
FIG. 8 is a refrigerant piping system diagram showing an embodiment of the sixth invention. 1...Compressor, 1a...Suction port, 1b...Discharge port, 1
4, 15... Frame, 16... Cylinder, 16a... Cylinder chamber, 23... Four-way switching valve, 28... First gas pipe,
29...Second gas pipe, 50...First bypass path, 60
...Second bypass path, 64...Intermediate position of second bypass path, 70...Opening/closing valve, 71...Back chamber, 80...Solenoid valve, 90...Capillary, 81...First solenoid valve, 82
...Second electromagnetic valve, 91...First capillary, 92...Second capillary, 93...Third capillary, 94...Fourth capillary.

Claims (1)

[Scope of Claims] 1. Within the frame of the compressor 1, one end opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end communicates with the suction port 1a. A first bypass passage 50 is provided, and an on-off valve 70 for opening and closing the first bypass passage 50 is provided in the first bypass passage 50, and a tubular body is disposed outside the frame of the compressor 1. One end of the body communicates with the low pressure side and the other end communicates with the high pressure side to form a second bypass path 60, and an intermediate position 64 of the second bypass path 60 communicates with the back chamber 71 of the on-off valve 70. Meanwhile, a solenoid valve 80 is interposed between the intermediate position 64 and the low pressure side of the second bypass path 60, and a capillary reach tube 90 is interposed between the intermediate position 64 and the high pressure side, The solenoid valve 8
1. A refrigeration system characterized in that the capacity of the compressor 1 is controlled by opening and closing 0. 2. One end of the tubular body forming the second bypass passage 60 is connected to the suction passage 6 in the refrigeration cycle, and the other end is connected to the discharge passage 7, so that between the suction passage 6 and the discharge passage 7, The refrigeration system according to claim 1, characterized in that the second bypass path 60 is formed. 3 Solenoid valve 80 installed in the second bypass path 60
The solenoid valve 80 is closed when energized and opened when not energized, and when the refrigeration operation is stopped, the solenoid valve 80 is always open to equalize the high and low pressures in the refrigeration cycle. Refrigeration equipment according to scope 1 or 2. 4. A four-way switching valve 23 is connected between the inlet and outlet of the compressor 1, and by switching the four-way switching valve 23, the refrigerant flow direction is reversible and configured as a refrigeration system capable of heating and cooling. A first bypass passage 50 is provided inside the cylinder 16, one end of which opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end of which communicates with the suction port 1a. road 50, the first bypass road 50
In addition to providing an on-off valve 70 for opening and closing, a tubular body is provided outside the frame of the compressor 1, and one end of the tubular body is connected to the first gas pipe 28, which has a high pressure during cooling and a low pressure during heating. , the other end is connected to a second gas pipe 29 which has a low pressure during cooling and a high pressure during heating to form a second bypass path 60 between the first and second gas pipes 28 and 29. An intermediate position 64 of the second bypass passage 60 is communicated with the back chamber 71 of the on-off valve 70, and an electromagnetic conductor is connected between the intermediate position 64 of the second bypass passage 60 and the connection position to the first gas pipe 28. A valve 80 is interposed, and a capillary reach tube 90 is interposed between the intermediate position 64 and the connection position to the second gas pipe 29,
A refrigeration system characterized in that the capacity of the compressor 1 is controlled by opening and closing the electromagnetic valve 80. 5 Solenoid valve 80 installed in the second bypass path 60
is closed when energized and opened when not energized, and when the refrigeration operation is stopped, the solenoid valve 80 is always open to equalize the high and low pressures in the refrigeration cycle. Refrigeration equipment according to scope 4. 6. A first bypass passage 50 is provided in the frame of the compressor 1, one end of which opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end of which communicates with the suction port 1a. An on-off valve 70 for opening and closing the first bypass path 50 is provided in the first bypass path 50, and a tubular body is provided outside the frame of the compressor 1, with one end of the tubular body connected to the low pressure side. and the other end communicates with the high pressure side to form a second bypass passage 60, and an intermediate position 64 of the second bypass passage 60 communicates with the back chamber 71 of the on-off valve 70, while the other end communicates with the high pressure side. A first solenoid valve 81 is provided between the intermediate position 64 of the two bypass passage 60 and the low pressure side,
Further, a capillary reach tube 90 and a second solenoid valve 82 are interposed between the intermediate position 64 and the high pressure side, and the first and second solenoid valves 81, 82 are interposed between the intermediate position 64 and the high pressure side.
A refrigeration system characterized in that the capacity of the compressor 1 is controlled by opening and closing the refrigeration system. 7 One end of the tubular body forming the second bypass path 60 is connected to the suction passage 6 in the refrigeration cycle, and the other end is connected to the discharge passage 7, so that between the suction passage 6 and the discharge passage 7, 7. The refrigeration system according to claim 6, wherein the second bypass path 60 is formed. 8 First and second interposed in the second bypass path 60
The solenoid valves 81 and 82 are closed when energized and opened when de-energized, so that when the refrigeration operation is stopped, each of the solenoid valves 8
8. A refrigeration system according to claim 6 or 7, characterized in that ports 1 and 82 are always open to equalize high and low pressures in the refrigeration cycle. 9. A four-way switching valve 23 is connected between the inlet and outlet of the compressor 1, and the refrigerant flow direction is reversible by switching the four-way switching valve 23, thereby forming a refrigeration system capable of heating and cooling. One end opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16.
A first bypass passage 50 communicating with a is provided, an on-off valve 70 for opening and closing the first bypass passage 50 is provided in this first bypass passage 50, and a tubular body is disposed outside the frame of the compressor 1. One end of the tubular body is connected to a first gas pipe 28 that has high pressure during cooling and low pressure during heating, and the other end is connected to a second gas pipe 29 that has low pressure during cooling and high pressure during heating. Between the first and second gas pipes 28 and 29,
A second bypass passage 60 is formed, an intermediate position 64 of the second bypass passage 60 is communicated with the back chamber 71 of the on-off valve 70, and the intermediate position 64 of the second bypass passage 60 and the first gas pipe 28 are connected to each other. A first solenoid valve 81 is interposed between the connecting position to the connecting position, and a capillary reach tube 90 and a second solenoid valve 82 are interposed between the intermediate position 64 and the connecting position to the second gas pipe 29. and the first and second solenoid valves 81, 82
A refrigeration system characterized in that the capacity of the compressor 1 is controlled by opening and closing the refrigeration system. 10 The first and second solenoid valves 81 and 82 installed in the second bypass path 60 are closed when energized and opened when not energized, so that when the refrigeration operation is stopped, each of the solenoid valves 8
1. The refrigeration system according to claim 9, wherein the refrigeration cycle is always open to equalize the high and low pressures in the refrigeration cycle. 11 A four-way switching valve 23 is connected to the inlet/outlet side of the compressor 1, and by switching the four-way switching valve 23, the flow direction of the refrigerant is reversible, thereby forming a refrigeration system capable of heating and cooling. A first bypass passage 50 is provided, one end of which opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b of the cylinder 16, and the other end of which communicates with the suction port 1a. 50, the first bypass path 50
In addition to providing an on-off valve 70 for opening and closing, a tubular body is provided outside the frame of the compressor 1, and one end of the tubular body is connected to the first gas pipe 28, which has a high pressure during cooling and a low pressure during heating. , the other end is connected to a second gas pipe 29 which has a low pressure during cooling and a high pressure during heating, and between the first and second gas pipes 28 and 29,
While forming the second bypass path 60, this second bypass path 60 is formed.
The intermediate position 64 of the bypass path 60 is connected to the on-off valve 7.
A first electromagnetic valve 81 and a first capillary reach tube 91 are connected to the rear chamber 71 of the second bypass passage 60 and between the intermediate position 64 of the second bypass passage 60 and the connection position to the first gas pipe 28, Also, the intermediate position 64
and the connection position to the second gas pipe 29.
A check valve 10 that includes a capillary reach tube 92 and a second electromagnetic valve 82, and allows the capillary reach tubes 91 and 92 to flow only from the intermediate position 64 to the gas pipes 28 and 29.
0 and 101 are provided in parallel, respectively, and the capacity of the compressor 1 is controlled by opening and closing the first and second solenoid valves 81 and 82. 12 The first and second solenoid valves 81 and 82 installed in the second bypass path 60 are closed when energized and opened when not energized, so that when the refrigeration operation is stopped, each of the solenoid valves 8
12. The refrigeration system according to claim 11, wherein ports 1 and 82 are always open to equalize the high and low pressures in the refrigeration cycle. 13 Inside the frame of the compressor 1, one end is connected to the cylinder 16.
A first bypass passage 50 is provided which opens into the cylinder chamber 16a at an intermediate portion between the suction port 1a and the discharge port 1b, and whose other end communicates with the suction port 1a. An on-off valve 70 for opening and closing the bypass passage 50 is provided, and a tubular body is disposed outside the frame of the compressor 1, one end of the tubular body is communicated with the low pressure side, and the other end is communicated with the high pressure side, A second bypass passage 60 is formed, and an intermediate position 64 of the second bypass passage 60 is communicated with the back chamber 71 of the on-off valve 70, while the intermediate position 64 of the second bypass passage 60 and the low pressure side are connected to each other. Between the first solenoid valve 81 and
Furthermore, two third and fourth capillary reach tubes 93, 94 are provided between the intermediate position 64 and the high pressure side.
and a second solenoid valve 82 connected in parallel with the fourth capillary reach tube 94, respectively, so that the first
A refrigeration system characterized in that the capacity of the compressor 1 is controlled by opening and closing second electromagnetic valves 81 and 82. 14 The first solenoid valve 81 installed in the second bypass path 60 is closed when energized and opened when not energized, so that when the refrigeration operation is stopped, the first solenoid valve 81 is always open and the refrigeration cycle is stopped. 14. A refrigeration system according to claim 13, characterized in that pressure is equalized between high and low pressures.