JP4945306B2 - Scroll compressor and heat pump device using the same - Google Patents

Description

  The present invention relates to a scroll compressor and a heat pump device such as a refrigeration air conditioner and a heat pump water heater using the same.

  Conventionally, as described in Patent Document 1, the rear surface of the end plate of the orbiting scroll is partitioned into an annular outer back pressure chamber, a central back pressure chamber, and an inner back pressure chamber, and the outer back pressure chamber is defined as a compression chamber. The central back pressure chamber communicates with the refrigerant suction section, the central back pressure chamber communicates with the discharge chamber, and the inner back pressure chamber communicates with the motor chamber to prevent tilting of the revolving end plate at the start of operation, and the revolving scroll is pushed against the fixed scroll. A scroll compressor having a structure to be attached was described.

JP 2000-205154 A

  The scroll compressor described in Patent Document 1 has a structure in which the pressure in the central back pressure chamber that generates the largest back pressure that presses the orbiting scroll against the fixed scroll from the back is adjusted by a constant throttle.

  However, when it is used in a refrigerant cycle using a scroll compressor having such a structure, such as a heat pump water heater, the pressure condition of the scroll compressor varies greatly depending on the required hot water discharge capacity, the orbiting scroll is used. Was found to be insufficient to provide adequate back pressure.

  Taking an example of the pressure condition of the heat pump water heater, the discharge pressure from the compressor varies greatly under the pressure condition of discharging at 42 ° C. and the pressure condition of discharging at 90 ° C.

  Under such conditions, if the pressure applied to the back of the orbiting scroll under the 42 ° C. hot water condition (pressure that presses the orbiting scroll against the fixed scroll; hereinafter referred to as back pressure) is optimized, the back pressure will be reduced under the 90 ° C. hot water condition. It becomes too high and excessively presses the orbiting scroll against the fixed scroll, increasing the sliding loss and lowering the efficiency.

  Similarly, if the back pressure applied to the orbiting scroll under the 90 ° C. hot water condition is optimized, the back pressure is smaller than the pressure in the compression chamber formed by the orbiting scroll and the fixed scroll under the 42 ° C. hot water condition, and the orbiting scroll is fixed. There was a problem that the pressing force to the scroll was insufficient, the operation at the time of start-up became unstable, and the leakage from the compression chamber increased during the normal operation and the efficiency was lowered.

In order to solve the above-described problems, a scroll compressor according to the present invention includes a orbiting scroll, a fixed scroll that meshes with the orbiting scroll to form a compression chamber, a frame to which the fixed scroll is fixed, an orbiting scroll, a fixed scroll, and a frame. An intermediate pressure chamber formed by the orbiting scroll, a communication hole communicating with the compression chamber and the intermediate pressure chamber, a communication hole opening / closing means for opening and closing the communication hole, and a low-pressure fluid from the outside. Pressure of the intermediate pressure chamber adjusted by the communication path opening / closing means The communication hole communicates with the compression chamber having a smaller pressure .
Alternatively, the scroll compressor according to the present invention is formed by a orbiting scroll, a fixed scroll that meshes with the orbiting scroll to form a compression chamber, a frame to which the fixed scroll is fixed, and the orbiting scroll, the fixed scroll, and the frame. An intermediate pressure chamber, a communication hole provided in the orbiting scroll and communicating the compression chamber and the intermediate pressure chamber, and the communication hole according to a difference between the pressure of the compression chamber and the pressure of the intermediate pressure chamber A communication hole opening / closing means for opening and closing, a suction pressure space into which a low-pressure fluid from the outside is introduced, a communication passage communicating the intermediate pressure chamber and the suction pressure space, and the pressure of the intermediate pressure chamber and the suction pressure A communication passage opening / closing means for opening and closing the communication passage according to a difference from the pressure in the space, and the communication passage opening / closing means has It is lower than the intermediate pressure to open the communication passage.

In order to solve the above problems, a heat pump device according to the present invention includes a scroll compressor, a heat exchanger that performs heat exchange between water flowing through the water passage and refrigerant flowing through the refrigerant passage, and heat exchange with the heat exchanger. An expansion valve for decompressing the decompressed refrigerant and an evaporator for evaporating the decompressed refrigerant are connected to each other by a refrigerant pipe, and the scroll compressor is fixed to form an orbiting scroll and the orbiting scroll to engage with each other to form a compression chamber. A scroll, a frame to which the fixed scroll is fixed, an intermediate pressure chamber formed by the orbiting scroll, the fixed scroll, and the frame; and a communication that is provided in the orbiting scroll and communicates the compression chamber and the intermediate pressure chamber. a hole, a communicating hole opening and closing means for opening and closing the communication hole, and between the suction pressure of the fluid of the low pressure from the outside is introduced, the intermediate-pressure chamber and the suction pressure A communication passage that communicates with each other, and a communication passage opening and closing means that opens and closes the communication passage, and the scroll compressor has a pressure smaller than the pressure of the intermediate pressure chamber adjusted by the communication passage opening and closing means. The communication hole communicates with the compression chamber .

  According to the present invention, the scroll compressor of the present invention can surely press the orbiting scroll against the fixed scroll even at the time of activation, and can prevent the orbiting scroll from being detached.

  Moreover, the heat pump device equipped with the scroll compressor of the present invention has high reliability and excellent energy efficiency.

  FIG. 1 is a longitudinal sectional view of a horizontal scroll compressor according to a first embodiment of the present invention. Specifically, it is a diagram seen from a plurality of cross-sections for each component of the orbiting scroll 101, the fixed scroll 102, the frame 109, and the Oldham ring 110, which will be described later.

  2 is a cross-sectional view taken along the line AA of FIG. 1 as viewed from the scroll wrap 102n side of the fixed scroll 102. FIG.

  3 is an enlarged view of the differential pressure control valve 108, FIG. 4 is a view seen from the scroll wrap 101b side of the orbiting scroll 101, FIG. 5 is a cross-sectional view of the orbiting scroll 101 taken along the line BB in FIG. FIG. 7 is an explanatory diagram when the communication valve 127 is open, FIG. 8 is an explanatory diagram when the communication valve 127 is closed, and FIG. 9 is a state diagram of an intermediate pressure within the operating pressure range of the compressor.

  First, the structure will be described. In FIG. 1, the orbiting scroll 101 has a scroll wrap 101b standing on an end plate 101a. On the rear surface of the end plate 101a, there are provided a bearing holding portion 101d into which a turning bearing 101c is inserted and a turning Oldham groove 101e.

  As shown in FIG. 2, the fixed scroll 102 has a fixed scroll reference surface 102a that is the same surface as the tooth tip surface of the scroll wrap 102n. A peripheral groove 102b is provided on the fixed scroll reference surface 102a. The tooth bottom (the surface between the scroll wrap 102n and the fixed scroll reference surface 102a) has four release holes 102c.

  The scroll wrap 101b meshes with the scroll wrap 101b of the orbiting scroll 101 and the scroll wrap 102n of the fixed scroll 102, and the orbiting scroll 101 orbits to move the compression chamber 103 made of the orbiting scroll 101 and the fixed scroll 102 from the outside to the inside. While reducing the volume, the working refrigerant in the compression chamber 103 is compressed.

  The scroll wraps slide through the refrigerating machine oil, and the tip of the scroll wrap 101b of the orbiting scroll 101 (the surface facing the fixed scroll 102 of the scroll wrap 101b), the bottom of the fixed scroll 102, and the scroll of the fixed scroll 102 The tooth tip of the wrap 102n (surface facing the orbiting scroll 101 of the scroll wrap 102n) and the tooth bottom (end plate 101a) of the orbiting scroll 101 also slide through the refrigerator oil. A closed space formed by each scroll wrap, the bottom of the fixed scroll 102 and the bottom of the orbiting scroll 101 is a compression chamber 103.

  The release hole 102c is for extracting the refrigerant gas from the release hole 102c when the pressure in the compression chamber 103 becomes equal to or higher than the discharge pressure.

  As shown in FIG. 1, a release valve plate 104 that is a reed valve plate that covers the release hole 102 c and opens when the pressure in the compression chamber 103 becomes equal to or higher than the discharge pressure, and the release valve plate 104. A retainer 104 a that limits the opening degree is fixed to an end surface of the fixed scroll 102 on the side opposite to the orbiting scroll 101 by a fixing screw 105. A discharge hole 102d is opened near the center of the end face.

  In addition, as shown in FIG. 2, the fixed scroll 102 has a portion of the suction pressure space to which the low-pressure refrigerant gas (working fluid) introduced from the outside of the machine is supplied into the compression chamber 103 on the outer edge side of the tooth bottom surface 102q. It has a suction dig 102e. A suction hole 102f (indicated by a dotted line in the figure) for inserting the suction pipe 106 from the back surface (the mounting surface of the release valve plate 104) communicating with the suction well 102e is formed on the back side of the fixed scroll 102. Provide.

  A suction pipe 106 is inserted into the suction hole 102f communicating with the suction pressure space through a suction side check valve 107 including a valve body 107a and a check valve spring 107b. The suction-side check valve 107 closes the gas flow path when the gas pressure in the suction port 116 through which the low-pressure gas sucked into the compression chamber 103 passes becomes higher than the pressure in the suction pipe 106.

  Further, on the outer periphery of the fixed scroll 102, there are provided a plurality of flow grooves 102g through which discharge gas discharged from the discharge holes 102d and refrigerating machine oil separated from the gas in the fixed back chamber 117 flow to the motor 112 side.

  Next, the differential pressure control valve 108 that controls the pressure difference between the back pressure region and the suction pressure region will be described. 2 and 3, a valve hole 102h is provided in the fixed scroll 102, and a valve seal 102i having a penetrating hole is provided on the orbiting scroll 101 side. And from the side surface of this valve hole 102h, it has the suction side conduction | electrical_connection path 102k connected to R groove | channel 102m which makes a part of suction pressure space.

  In FIG. 3, the valve hole 102h is provided with a valve body 108a for closing a hole provided in the valve seal 102i having a valve seal surface, and a differential pressure valve spring 108b for pressing the valve body 108a. In order to fix the differential pressure valve spring 108b, a valve press-fitted into a valve cap insertion portion 102l having a diameter larger than that of the valve hole 102h in a state where one end of the differential pressure valve spring 108b is inserted into a spring positioning protrusion 108c provided on the valve cap 108d. A cap 108d is provided.

  Next, the frame 109 will be described. The frame 109 has a fixed attachment surface 109a for attaching the fixed scroll 102 to the outer periphery, and a turning scroll sandwiching surface 109b on the inner side. Further inside, an Oldham ring 110 for preventing rotation of the orbiting scroll 101 is provided between the frame 109 and the orbiting scroll 101 so as to have a frame Oldham groove 109c.

  In addition, a shaft seal 109d that slides with the shaft 111 and a main bearing 109e that slides and receives a bearing with the shaft 111 are provided in the center of the frame 109, and the shaft that receives the shaft 111 on the orbiting scroll 101 side. A thrust surface 109f is provided. On the outer peripheral surface of the frame 109, a plurality of flow grooves 109 h that are in communication with a plurality of flow grooves 102 g provided on the outer periphery of the fixed scroll 102 and serve as gas and oil flow paths are provided.

  A frame side protrusion 110a is provided on one surface of the Oldham ring 110, which is a substantially circular ring, and a turning scroll side protrusion 110b is provided on the other surface.

  The shaft 111 includes a shaft oil supply hole 111a that penetrates the shaft 111, a main bearing oil supply hole 111b that communicates with the shaft oil supply hole 111a and opens to face the main bearing 109e, and a shaft seal 109d that communicates with the shaft oil supply hole 111a. A shaft seal oil supply hole 111c that opens to face the shaft 111 and a sub bearing oil supply hole 111d that opens to face the sub bearing 113 that communicates with the shaft oil supply hole 111a and receives the shaft 111 are provided.

  An eccentric portion 111e, which is one end portion of the shaft 111, is inserted into the swing bearing 101c, and one end portion is inserted into the auxiliary bearing 113.

  The sub bearing 113 is incorporated in a sub bearing housing 115, and the sub bearing housing 115 is fixed to a sub bearing support plate 114 fixed to the hermetic container 122.

  Further, a rotor 112 a is press-fitted into the shaft 111, and the motor 112 is formed by the rotor 112 a and the stator 112 b that is shrink-fitted into the sealed container 122.

  Next, the operation of the scroll compressor in this embodiment will be described. As the stator 112b is energized and the rotor 112a rotates, the shaft 111 rotates. As the shaft 111 rotates, the eccentric portion 111e transmits a driving force to the orbiting bearing 101c, and the orbiting scroll 101 orbits. Since the Oldham ring 110 is provided, rotation of the orbiting scroll 101 is prevented.

  By this operation, the refrigerant gas in the suction port 116 sucked from the outside of the compressor through the suction pipe 106 enters the compression chamber 103 formed between both scrolls and is compressed and discharged from the discharge hole 102d to the fixed back chamber 117. Is done.

  The refrigerant gas discharged into the fixed back chamber 117 enters the motor chamber 118 through the fixed scroll 102 and the flow grooves 102g and 109h in the outer periphery of the frame.

  The refrigerant gas that has entered the motor chamber 118 passes through a gap of the motor 112 (such as a coil of the stator 112b or a gap between the stator 112b and the rotor 112a). In the process, the refrigerant gas mixed with the refrigerating machine oil in the compression chamber 103 collides with the rotor 112a and the stator 112b, and the refrigerating machine oil contained in the refrigerant gas is separated. The separated oil falls and accumulates in an oil pool below the motor chamber 118.

  The refrigerant gas entering the motor chamber 118 passes through the vent hole 114a provided in the auxiliary shaft support plate 114, collides with the oil separation plate 125, further separates the oil contained therein, and is discharged from the discharge pipe 120 to the outside. Get out.

  With the pressure of the refrigerant gas in the motor chamber 118 and the pressure of the refrigerant gas in the oil storage chamber 121, the pressure in the oil storage chamber 121 is lower than the pressure in the motor chamber 118 due to the flow path resistance passing through the vent hole 114 a. As a result, the refrigerating machine oil 119 in the motor chamber 118 is pushed out from the oil guide hole 114 b of the countershaft support plate 114, and the oil level of the oil storage chamber 121 becomes higher than the oil level of the motor chamber 118.

  Next, refueling will be described. Refrigerating machine oil is supplied to the intermediate pressure chamber 123 formed by the orbiting scroll 101, the fixed scroll 102, and the frame 109 through the gap between the main bearing 109e and the shaft 111 due to the differential pressure between the discharge pressure and the suction pressure. As the operation time of the compressor elapses, the pressure in the intermediate pressure chamber 123 gradually increases, and the pressure between the suction pressure and the discharge pressure (hereinafter referred to as intermediate pressure) by the differential pressure control valve 108. Corresponds to the aforementioned back pressure).

  The refrigerating machine oil 119 in the oil storage chamber 121 in the discharge pressure atmosphere is decentered from the oil supply pipe 124 through the shaft oil supply hole 111a due to the differential pressure between the discharge pressure in the oil storage chamber 121 and the intermediate pressure in the intermediate pressure chamber 123. The revolving bearing 101c is supplied with oil from the opening at the tip of 111e.

  Further, the sliding force is supplied from the main bearing oil supply hole 111b, the shaft seal oil supply hole 111c, and the sub-bearing oil supply hole 111d to the sliding portions by the centrifugal force generated by the rotation of the shaft 111. The refrigerating machine oil 119 supplied to the slewing bearing 101 c leaks into the intermediate pressure chamber 123 and enters the suction port 116 from the differential pressure control valve 108 and lubricates the inside of the compression chamber 103. The refrigerating machine oil 119 that did not contribute to lubrication is discharged into the fixed back chamber 117 together with the refrigerant gas.

  Next, the relationship between the orbiting scroll 101 and the communication valve 127 will be described. 4, 5, and 6, the orbiting scroll 101 has a communication hole 126 in the end plate 101a outside the scroll wrap 101b and in the vicinity of the scroll wrap 101b. A pressure between the compression chamber 103 and the intermediate pressure chamber 123 is adjusted by the communication valve 127 through the communication hole 126. The communication hole 126 has an opening on the compression chamber 103 side at a position where the compression chamber 103 is formed by the fixed scroll 102 and the orbiting scroll 101 by the orbiting scroll 101 turning.

  The communication valve 127 is provided in the end plate 101a. In the communication valve hole 127a that communicates with the communication hole 126, a communication valve body 127b that closes the communication hole 126 in the end plate 101a, and a communication valve that presses the communication valve body 127b. Opening / closing means having a spring 127c.

  Furthermore, the communication valve 127 has a communication valve cap 127e provided with a communication spring positioning protrusion 127d for inserting one end of the communication valve spring 127c. The communication valve cap 127e communicates with the communication valve hole 127a and is press-fitted into a communication valve cap insertion portion 127f having a diameter larger than that of the communication valve hole 127a.

  The communication valve cap 127e is preferably provided with a plurality of flow paths through which the refrigerant gas passes, and the cross sectional area of the flow paths combined is larger than the flow path cross sectional area of the communication hole 126.

  The communication valve body 127 b opens and closes due to the differential pressure between the compression chamber 103 and the intermediate pressure chamber 123. The spring force of the communication valve spring 127c poses no problem as long as the communication valve body 127b can be normally opened and closed. However, as will be described later, the spring of the communication valve spring 127c can open the communication hole 126 with a predetermined differential pressure. Set the force.

  Further, the communication valve spring 127c may be provided with a shape that can be normally opened and closed by the communication valve body 127b itself, for example, a flexible spring portion that generates a pressing force on the communication hole 126. In this case, the communication valve spring 127c may not be provided.

  If such a communication valve 127 is provided in the orbiting scroll 101 and the balance with respect to the orbiting bearing 101c becomes worse, a weight may be provided on the intermediate pressure chamber 123 side of the orbiting scroll 101 or a balance adjusting hole may be provided.

  Further, in this embodiment, the intermediate communication hole 126 is provided outside the scroll wrap 101b in the orbiting scroll 101 in FIG. 4, but as shown in FIG. 10, the positions of the intermediate communication hole 126 and the communication valve 127 (not shown) are turned. You may provide inside the scroll wrap 101b of the scroll 101. FIG.

  Even in the configuration using the orbiting scroll of FIG. 10, since the refrigerant gas compressed from the compression chamber 103 can be supplied to the intermediate pressure chamber 123 at the time of startup, the pressure in the intermediate pressure chamber 123 is likely to increase. As a result, the orbiting scroll 101 can be surely pressed against the fixed scroll 102 and the orbiting scroll 101 can be prevented from being detached.

  The same effect can be obtained even when independent communication holes 126 are provided outside and inside the scroll wrap 101b of the orbiting scroll 101, respectively.

  Next, the operation of the communication valve 127 will be described with reference to FIGS.

  When the compressor is stopped, the compression chamber 103 and the intermediate pressure chamber 123 are at the same pressure, and the communication hole 126 is closed in the communication valve body 127b by the spring force of the communication valve spring 127c (FIG. 8). Yes.

  When the compressor is started, the pressure in the compression chamber 103 starts to rise, and the communication valve body 127b is opened due to the influence (FIG. 7), and a refrigerant gas flows from the compression chamber 103 to the intermediate pressure chamber 123. The pressure in the intermediate pressure chamber 123 increases.

  Due to the effect of the pressure difference between the compression chamber 103 side and the intermediate pressure chamber 123 side of the orbiting scroll 101, the orbiting scroll 101 presses against the fixed scroll 102 because a self-separation avoiding action acts on the orbiting scroll 101 itself.

  After the start-up, as described above, the refrigeration oil is supplied through the gap between the main bearing 109e and the shaft thrust surface 109f, and the pressure in the intermediate pressure chamber 123 increases. When the pressure in the intermediate pressure chamber 123 becomes higher than that in the compression chamber 103 through which the communication hole 126 communicates, the differential pressure control valve 108 adjusts. That is, the intermediate pressure of the refrigerant gas is adjusted not only by the communication valve 127 but also by the differential pressure control valve 108.

  Next, the state of the intermediate pressure within the operating pressure range of the scroll compressor of the present embodiment will be described using FIG. 9 by showing the relationship between the suction pressure and the intermediate pressure in the differential pressure control valve 108 and the communication valve 127. . The horizontal axis in FIG. 9 indicates the suction pressure, and the vertical axis indicates the intermediate pressure.

  As shown in FIG. 9, in the operating pressure range of the scroll compressor in this embodiment, the intermediate pressure formed by the communication valve 127 that is the opening / closing means of the communication hole 126 is formed by the differential pressure control valve 108. Set smaller than the intermediate pressure.

  In the operating pressure range of the scroll compressor in this embodiment, the intermediate pressure (line A) adjusted by the communication valve 127 is a pressure range that is smaller than the intermediate pressure (line B) adjusted by the differential pressure control valve 108. drive. In FIG. 9, the intersection of line A and line B overlaps with the maximum value of the operating pressure range, but this intersection may be included in the operating pressure range.

  In the operating pressure range of the scroll compressor in the present embodiment, the refrigerant gas compressed from the compression chamber 103 can be supplied to the intermediate pressure chamber 123 at the time of start-up, and therefore the pressure in the intermediate pressure chamber 123 tends to increase. Thereby, the orbiting scroll 101 is surely pressed against the fixed scroll 102, and the orbiting scroll 101 can be prevented from being detached.

  Further, when the operation of the scroll compressor is continued and the stable state of the refrigerant cycle to which the scroll compressor is connected, the communication valve body 127b is closed and the intermediate pressure is adjusted by the differential pressure control valve 108. Moreover, stable performance can be ensured even if there are a plurality of operating pressure conditions as in a heat pump water heater.

  The change in the intermediate pressure of the scroll compressor in the present embodiment will be described in more detail together with the operation state. After the scroll compressor is started, the communication valve 127 of the communication hole 126 is first operated to increase the intermediate pressure in the intermediate pressure chamber 123. Further, the intermediate pressure gradually increases when the refrigerating machine oil having the same pressure as the discharge pressure passing through the shaft 111 is reduced in pressure while passing through the gap between the bearings and supplied to the intermediate pressure chamber 123.

  Then, since the differential pressure between the intermediate pressure in the intermediate pressure chamber 123 and the suction pressure at the suction port 116 also increases, the intermediate pressure chamber 123 becomes higher than the pressure of the refrigerant gas compressed in the compression chamber 103 with which the communication hole 126 communicates. The refrigerant gas pressure is higher.

  If only the time of starting the scroll compressor is taken into consideration, the pressure is not increased by adjusting the spring force of the communication valve spring 127c so that at least the communication hole 126 is easily opened into the compression chamber 103. Higher pressure than the intermediate pressure chamber 123 can be supplied from the compression chamber 103 to the intermediate pressure chamber 123. Thereby, it is possible to prevent the orbiting scroll 101 from being detached from the fixed scroll 102 due to insufficient pressure in the intermediate pressure chamber 123.

  However, when the pressure in the intermediate pressure chamber 123 is controlled during operation, an unnecessarily high pressure is applied to the intermediate pressure chamber 123 depending on the position of the opening on the compression chamber 103 side of the communication hole 126. Then, the orbiting scroll 101 is pressed against the fixed scroll 102, and there is a possibility that the performance is lowered or the orbiting scroll 101 is stopped.

  Therefore, when the pressure in the intermediate pressure chamber 123 becomes higher than the pressure in the compression chamber 103 with which the communication hole 126 communicates, the spring of the communication valve spring 127c is operated so that the compressor operates with the communication valve body 127b closed (FIG. 8). The force was set and the intermediate pressure was adjusted only by the differential pressure control valve 108.

  In comparison with the same suction pressure in FIG. 9, if the intermediate pressure formed by the communication valve 127 is lower than the intermediate pressure formed by the differential pressure control valve 108, the intermediate pressure is controlled by the communication valve 127. Since the intermediate pressure can be controlled by the differential pressure control valve 108 when the above range is exceeded, stable performance can be ensured from the start of the scroll compressor to the stable operating state.

  However, contrary to the relationship shown in FIG. 9, if the intermediate pressure formed by the communication valve 127 is higher than the intermediate pressure formed by the differential pressure control valve 108, the intermediate pressure is controlled by the differential pressure control. When the range controlled by the valve 108 is exceeded, the differential pressure control valve 108 does not work, the intermediate pressure becomes too high, and the input to the compressor increases, causing performance degradation.

  Therefore, as shown in FIG. 9, when the intermediate pressure formed by the communication valve 127 is compared with the same suction pressure, the operation pressure range is lower than the intermediate pressure formed by the differential pressure control valve 108. It is preferred to operate to control the scroll compressor. In other words, when compared at the same suction pressure, the intermediate pressure at which the communication valve 127 opens the communication hole 126 is lower than the intermediate pressure at which the differential pressure control valve 108 opens the suction side conduction path 102k.

  By configuring the scroll compressor as described above, the pressure in the intermediate pressure chamber 123 can be easily increased at the time of startup, and the orbiting scroll 101 can be reliably pressed against the fixed scroll 102 and the orbiting scroll 101 can be prevented from being detached. Further, in the stable state of the cycle, the communication valve body 127b is closed and an intermediate pressure is formed by the differential pressure control valve 108. Therefore, even if there are a plurality of operating pressure conditions such as a heat pump device, for example, a heat pump water heater, Stable performance can be secured.

  Next, an embodiment of the refrigerant cycle using the scroll compressor in the present embodiment will be described. In the present embodiment, a refrigerant cycle when the above-described scroll compressor is applied to a heat pump water heater will be described with reference to FIG.

  In this example, carbon dioxide was used as the working refrigerant, and polyalkylene glycol oil (PAG) or polyalphaolefin oil (PAO) was used as the refrigerating machine oil. The refrigerating machine oil is not limited to these as long as it has performance equivalent to these.

  In FIG. 11, the scroll compressor 200 of the present embodiment, the heat exchanger 201 that performs heat exchange between the water flowing through the water passage 202 and the refrigerant flowing through the refrigerant passage 203, and the expansion that decompresses the refrigerant that has exchanged heat with the heat exchanger 201. The valve 29 and the evaporator 30 for evaporating the decompressed refrigerant are connected by a sealed refrigerant pipe.

  The high-temperature and high-pressure refrigerant discharged from the scroll compressor 200 in this embodiment is supplied to the heat exchanger 201 and exchanges heat with water flowing through the water passage 202 in a flow opposite to the refrigerant. The refrigerant that exchanges heat with water is decompressed through the expansion valve 204 and sent to the evaporator 205.

  In the evaporator 205, heat exchange is performed between the air blown by the evaporator fan 206 and the liquefied refrigerant, and the low-temperature and low-pressure refrigerant returns to the scroll compressor 200 and is compressed again.

  The water heated by the heat exchanger 201 will be described. The clean water introduced through the water supply port 207 passes through the water passage 202 and is heated by the heat exchanger 201. The heated water becomes hot water and is discharged from a tap 213 serving as a faucet, a shower nozzle, or a bath hot water outlet.

  In the heat pump water heater shown in FIG. 11, the water introduced from the water supply port 207 is stored in the hot water storage tank 208 while being heated by the heat exchanger 201, and the tank hot water discharged from the hot water storage tank 208 is introduced from the water supply port 207. The apparatus is capable of both direct hot water that is heated directly by the heat exchanger 201 and discharged from the hot water outlet 213, and tank hot water mixed hot water that combines them.

  In the case of tank hot water, water supplied from the water supply port 207 is temporarily stored in the hot water storage tank 208, and water is supplied from the lower part of the hot water storage tank 208 to the heat exchanger 201 using the pump 209. The water heated by the heat exchanger 201 is returned to the upper part of the hot water storage tank 208 through the tank hot water mixing valve 210 opened to the heat exchanger 201 and the hot water storage tank 208. The water heated by the heat exchanger 201 is stored from above in the hot water storage tank 208, and when it is detected by a sensor (not shown) that a predetermined amount of high temperature water has been stored in the hot water storage tank 208, the pump 209 Stop and stop the circulation of water in the hot water storage tank 208.

  The operation of the refrigerant cycle may start the operation of the scroll compressor 200 in accordance with the start of the operation of the pump 209. The operation of the refrigerant cycle may be stopped by gradually decreasing the number of rotations as the hot water in the hot water storage tank 208 is stored by the pump 209, or the operation is stopped when the rotation of the pump 209 is stopped. You may do it.

  Next, although it is direct hot water but the refrigerant cycle is not in a state necessary for heating the supplied water, the opening degree of the tank hot water mixing valve 210 is adjusted and the heat exchanger 201 The hot water is mixed with tank hot water and discharged.

  When the refrigerant cycle is in the required heating state, the hot water is discharged without mixing the hot water in the hot water tank mixing valve 210. It is preferable to adjust the opening degree of the tank hot water mixing valve 210 until the refrigerant cycle is sufficiently heated so as to gradually reduce the ratio of mixing the tank hot water. It can be controlled by detecting the temperature of the water coming out of the heat exchanger 201.

  Further, the temperature of the water that has passed through the tank hot water mixing valve 210 is detected, and when the temperature is higher than the set temperature, the water mixing valve 211 is adjusted to control so that unheated water is mixed and discharged. The water mixing valve 211 is also used when the hot water in the hot water storage tank 208 is discharged.

  The flow rate adjustment valve 212 is used to bring the water temperature closer to the set temperature than the water flow rate when the heating state that requires the refrigerant cycle has not been reached, or when the temperature of the water to be discharged does not reach the set temperature. When the flow rate of water is reduced, the opening degree is controlled to be reduced.

  In the heat pump water heater used in this way, the operation using the scroll compressor described above will be described.

  When the operation of the heat pump water heater shown in FIG. 11 is started, the scroll compressor 200 starts operation, the rotor 112a rotates, and the orbiting scroll 101 rotates through the shaft 111. As the compression chamber 103 formed by the orbiting scroll 101 and the fixed scroll 102 moves to the orbiting center, carbon dioxide as a refrigerant is compressed.

  The pressure in the intermediate pressure chamber 123 for pressing the orbiting scroll 101 against the fixed scroll 102 increases as carbon dioxide, which is a working refrigerant dissolved in the refrigeration oil, is gasified.

  The amount of carbon dioxide dissolved in PAG or PAO is less than the combination of R410A and polyol ester oil (POE) used in air conditioners and the like, and in the case of a combination of carbon dioxide and PAG or PAO, the back pressure is unlikely to increase. . As a result, the pressure in the intermediate pressure chamber 123 is insufficient at the time of startup, and the orbiting scroll 101 may not be pressed against the fixed scroll 102.

  However, by using the scroll compressor of this embodiment, when the compressor is started, the pressure in the compression chamber 103 starts to rise, and the communication valve body 127b is opened due to the influence, and the intermediate pressure from the compression chamber 103 is increased. The refrigerant gas flows into the chamber 123, and the pressure in the intermediate pressure chamber 123 increases. Due to the pressure difference between the compression chamber 103 side and the intermediate pressure chamber 123 side of the orbiting scroll 101, the orbiting scroll 101 is pressed against the fixed scroll 102.

  Further, after the start-up, refrigeration oil is supplied through the gap between the main bearing 109e and the shaft thrust surface 109f, and the pressure in the intermediate pressure chamber 123 increases. When the pressure in the intermediate pressure chamber 123 becomes higher than that in the compression chamber 103 through which the communication hole 126 communicates, the differential pressure control valve 108 adjusts.

  As described above, in the heat pump water heater shown in FIG. 11, the revolving scroll 101 can be surely pressed against the fixed scroll 102 even when using refrigerating machine oil having a small amount of carbon dioxide dissolved, such as a combination of carbon dioxide and PAG or PAO.

  Further, in the heat pump water heater shown in FIG. 11, as an example, in order to efficiently store hot water, the water in the hot water storage tank 208 is set to 90 ° C. or higher in the heat exchanger 201, and 42 ° C. is directly discharged from the heat exchanger 201. The operation of the scroll compressor 200 is controlled so that the hot water is discharged.

  Also in this case, the spring force of the communication valve spring 127c of the communication valve 127 is set to be smaller than the spring force of the differential pressure valve spring 108b of the differential pressure control valve 108 so that the relationship shown in FIG. Thus, the heat pump water heater of the present embodiment can provide a heat pump water heater with high reliability and excellent energy efficiency.

1 is a longitudinal sectional view of a horizontal scroll compressor according to a first embodiment of the present invention. AA arrow sectional drawing of FIG. The enlarged view of a differential pressure control valve. The figure seen from the scroll wrap side of a turning scroll. BB arrow sectional drawing of FIG. The communication valve enlarged view. Explanatory drawing at the time of the communication valve opening in a 1st Example. Explanatory drawing at the time of the communication valve close in a 1st Example. The state figure of the intermediate pressure in the operating pressure range of a compressor. The figure seen from the scroll wrap side of the turning scroll concerning the 2nd example of the present invention. The refrigerant | coolant cycle figure which mounted the scroll compressor of this invention in the heat pump water heater.

Explanation of symbols

101 orbiting scroll 101a end plate 101b, 102n scroll wrap 101c orbiting bearing 101d bearing holding portion 101e orbiting Oldham groove 102 fixed scroll 102a fixed scroll reference surface 102b peripheral groove 102c release hole 102d discharge hole 102e suction hole 102f suction hole 102g flow groove 102h valve Hole 102i Valve seal 102k Suction side conduction path 102l Valve cap insertion part 102m R groove 103 Compression chamber 104 Release valve plate 104a Retainer 105 Fixing screw 106 Suction pipe 107 Suction side check valves 107a, 108a Valve body 107b Check valve spring 108 Difference Pressure control valve 108b Differential pressure valve spring 108c Spring positioning projection 108d Valve cap 109 Frame 109a Fixed mounting surface 109b Orbiting scroll pinching surface 109c Groove 109d shaft seal 109e main bearing 109f shaft thrust surface 109h flow groove 110 Oldham ring 110a frame side protrusion 110b orbiting scroll side protrusion 111 shaft 111a shaft oil supply hole 111b main bearing oil supply hole 111c shaft seal oil supply hole 111d sub bearing oil supply hole 111e Eccentric part 112 Motor 112a Rotor 112b Stator 113 Sub bearing 114 Sub bearing support plate 114a Vent hole 114b Oil guide hole 115 Sub bearing housing 116 Suction port 117 Fixed back chamber 118 Motor chamber 119 Refrigerating machine oil 120 Discharge pipe 121 Oil storage chamber 122 Sealed container 123 Intermediate pressure chamber 124 Oil supply pipe 125 Oil separation plate 126 Communication hole 127 Communication valve 127a Communication valve hole 127b Communication valve body 127c Communication valve spring 127d Communication spring positioning protrusion 127e Communication valve key 127f Communication valve cap insertion part 200 Scroll compressor 201 Heat exchanger 202 Water passage 203 Refrigerant passage 204 Expansion valve 205 Evaporator 206 Evaporator fan 207 Water supply port 208 Hot water storage tank 209 Pump 210 Tank hot water mixing valve 211 Water mixing valve 212 Flow rate adjustment valve 213

Claims (4)

A orbiting scroll, a fixed scroll that meshes with the orbiting scroll to form a compression chamber, a frame to which the fixed scroll is fixed, an intermediate pressure chamber formed by the orbiting scroll, the fixed scroll, and the frame; and the orbiting scroll A communication hole communicating with the compression chamber and the intermediate pressure chamber, a communication hole opening / closing means for opening and closing the communication hole, a suction pressure space into which low-pressure fluid from the outside is introduced, and the intermediate pressure chamber A communication passage that communicates with the suction pressure space, and a communication passage opening and closing means that opens and closes the communication passage,
A scroll compressor in which the communication hole communicates with the compression chamber having a pressure smaller than the pressure of the intermediate pressure chamber adjusted by the communication passage opening / closing means . A orbiting scroll, a fixed scroll that meshes with the orbiting scroll to form a compression chamber, a frame to which the fixed scroll is fixed, an intermediate pressure chamber formed by the orbiting scroll, the fixed scroll, and the frame; and the orbiting scroll A communication hole communicating with the compression chamber and the intermediate pressure chamber, a communication hole opening and closing means for opening and closing the communication hole according to a difference between the pressure of the compression chamber and the pressure of the intermediate pressure chamber, Depending on the difference between the suction pressure space into which the low-pressure fluid is introduced, the intermediate pressure chamber communicating with the suction pressure space, and the pressure of the intermediate pressure chamber and the pressure of the suction pressure space. Communication passage opening and closing means for opening and closing the communication passage,
The scroll compressor in which the communication hole opening / closing means opens the communication hole is lower than the intermediate pressure in which the communication path opening / closing means opens the communication path. A heat exchanger that exchanges heat between the scroll compressor, water flowing through the water passage and refrigerant flowing through the refrigerant passage, an expansion valve that decompresses the refrigerant that has exchanged heat with the heat exchanger, and evaporates the decompressed refrigerant Each of the evaporators is connected by a refrigerant pipe, and the scroll compressor includes a orbiting scroll, a fixed scroll that meshes with the orbiting scroll to form a compression chamber, a frame to which the fixed scroll is fixed, and the orbiting scroll. An intermediate pressure chamber formed by the fixed scroll and the frame, a communication hole provided in the orbiting scroll, communicating the compression chamber and the intermediate pressure chamber, a communication hole opening / closing means for opening and closing the communication hole, and an external A suction pressure space into which a low-pressure fluid from is introduced, a communication passage communicating the intermediate pressure chamber and the suction pressure space, and a communication passage opening / closing means for opening and closing the communication passage; Has,
The scroll compressor is a heat pump device in which the communication hole communicates with the compression chamber having a pressure smaller than the pressure of the intermediate pressure chamber adjusted by the communication passage opening / closing means. The heat pump apparatus according to claim 3, wherein carbon dioxide is used as a working refrigerant and PAG or PAO is used as refrigeration oil.

Images