JP6147640B2 - Refrigerant switching valve and device provided with refrigerant switching valve - Google Patents

Description

  The present invention relates to a refrigerant switching valve and a device including the refrigerant switching valve.

  As background art of the present invention, there are inventions described in the following Patent Documents 1 to 4.

In Patent Document 1 (Japanese Patent No. 4112918),
[Claim 1] According to claim 1, "the valve seat plate through which the refrigerant inlet and the refrigerant outlet penetrate in the thickness direction, and the valve seat plate so as to cover a front surface side of a front surface side and a back surface side of the valve seat plate. In the valve device having a sealed case attached to the surface portion of the valve and a valve body that slides on the surface of the valve seat plate to open and close the inlet or the outlet, the inlet and the outlet Pipe insertion holes that communicate with each other are formed, and a pipe support plate that is stacked on the back side of the valve seat plate, and ends are fixed in the pipe insertion holes of the pipe support plate so that they are connected to the inlet and the outlet. An inflow pipe and an outflow pipe communicating with each other, and ends of the inflow pipe and the outflow pipe are brazed in the pipe insertion hole, and the valve seat plate The pipe support plate is laminated so that both ends thereof are displaced, and a step portion is formed on the outer peripheral edge of the joint surface. The outer peripheral side of the joint surface between the valve seat plate and the pipe support plate is a metal thin film. The metal thin film is a plating film applied in a state where the valve seat plate and the pipe support plate are laminated, and is melted by heat at the time of brazing and surface tension. The valve device is characterized in that the film thickness of the portion formed in the stepped portion is thicker than the film thickness of the portion formed in the other region due to concentration by .

  Patent Document 2 (Japanese Patent No. 4118034) discloses in claim 1 that “a part of a fluid passage including a fluid inflow pipe and an outflow pipe is formed and a valve port communicating with the inflow pipe or the outflow pipe is opened and closed. And a valve driving device having a main body in which a valve body for interrupting the flow of the fluid is provided, and a driving means for driving the valve body, wherein the inflow pipe corresponding to the inside of the main body case opens. A valve seat is formed around the valve port connecting the outflow pipe to the outside, and a through-hole is formed in one valve seat plate on which the valve seat is formed, and is installed inside the main body case. A fixed shaft that supports a rotating body and a rotor support shaft on which a rotor as the driving means is rotatably supported are respectively engaged, and the fixed shaft and the rotor support shaft are fixed to the valve seat plate by welding and the penetrating through. A hole is hermetically sealed, the rotating body is a gear that meshes with a rotor pinion formed in the rotor and transmits a driving force to the valve body, and the fixed shaft is a gear that rotatably supports the gear. A valve driving device characterized in that it is a shaft "is disclosed.

  Patent Document 3 (Japanese Patent No. 4183575) discloses in claim 1 that “a fluid inlet and a valve seat plate through which a fluid outlet penetrates in the thickness direction, and a front side and a rear side of the valve seat plate. Among the sealed case that covers the surface side, the inflow pipe and the outflow pipe fixed to the back surface side of the valve seat plate so as to communicate with the inflow port and the outflow port, and among the front surface side of the valve seat plate, To support a valve body that slides on an area where the outlet is formed to open and close the outlet, a motor for driving the valve body, and a rotor of the motor in a rotatable state A rotor support shaft fixed to the valve seat plate and a valve formed to be shorter and narrower than the rotor support shaft and fixed to the valve seat plate to support the valve body in a rotatable state. With body support shaft In the valve device, the valve seat plate is divided into a first plate constituent member and a second plate constituent member that constitute an area where the outflow port is formed in an in-plane direction of the valve seat plate. The second plate constituent member is a press-processed product, and a first shaft hole for fixing the rotor support shaft is formed, and the first plate constituent member is the second plate. It is a machined product that is thicker than the component member, and is joined to the second plate component member by brazing, and has a second shaft hole smaller than the first shaft hole for fixing the valve body support shaft. A valve device characterized in that it is formed "is disclosed.

Japanese Patent No. 4112918 Japanese Patent No. 4118034 Japanese Patent No. 4183075

  In the configurations described in Patent Document 1 and Patent Document 2, both ends of the rotor support shaft are respectively formed by through holes (lower shaft holes) provided in the valve seat plate and shaft holes (upper shaft holes) provided in the sealing case. In order to maintain the squareness accuracy of the valve seat plate and the shaft, a high degree of concentricity is required between the lower shaft hole and the upper shaft hole. Good positioning is required.

  According to Patent Literature 1, the height direction and the radial direction of the sealing case are positioned by a step formed on the outer peripheral edge of the valve seat plate. There is no provision regarding the step shape.

  According to Patent Document 2, the height direction of the sealing case is positioned by the height restriction of the rotor spindle, and the radial direction of the sealing case is positioned by the outer periphery of the valve seat plate. There is no description regarding the positioning of the sealing case by the step, and the positioning of the sealing case described in Patent Document 2 is significantly less in the contact area of the positioning of the sealing case than the positioning by the step of the valve seat plate. There is a problem that reliability of accuracy may be lowered.

  Further, since the valve body support shaft and the valve body are provided at positions deviating from the center of the valve seat plate to the outer peripheral side, the heat generated when welding the outer periphery of the valve seat plate and the sealing case (valve case) There exists a problem that it is easy to conduct to a body and a resin-made valve body rises in temperature, and is easy to thermally deform.

  In the configuration described in Patent Document 3, both ends of the rotor support shaft are respectively provided with a first shaft hole (lower center shaft hole) provided in the second plate constituent member and a shaft hole (upper center shaft provided in the sealing case). In order to maintain the squareness accuracy between the valve seat plate and the shaft, the first shaft hole (lower center shaft hole) and the sealed case shaft hole (lower center shaft hole) Since high coaxiality is required, it is necessary to position the sealing case with high accuracy with respect to the valve seat plate. The sealing case is positioned in the height direction and the radial direction of the sealing case by the steps formed on the outer peripheral edge of the valve seat plate, but there is no provision regarding the step shape of the valve seat plate suitable for positioning the sealing case.

  In view of the above circumstances, an object of the present invention is to provide a refrigerant switching valve with high assembly accuracy and improved reliability, and a device using the refrigerant switching valve.

In order to solve such a problem, it comprises a valve body, a valve case having an open end that covers the valve body, and a valve seat plate provided at one end of the valve case, the valve seat plate comprising: A first valve seat plate portion, and an outer peripheral valve seat plate portion that is provided on an outer periphery of the first valve seat plate portion and is thinner than the first valve seat plate portion, and the valve case includes the opening includes an enlarged portion formed by bending R toward the side, the height of the previous SL step formed between the outer peripheral valve seat plate portion and the first valve seat plate portion than the thickness of the outer peripheral valve seat plate portion The enlarged portion is located within the height dimension of the step, and the inner peripheral surface of the valve case formed above the enlarged portion is the first valve seat. By fitting with the step formed on the outer peripheral surface of the plate part, Said a Kiben case the first seat plate portion is positioned, characterized in that the weld portion and the outer periphery of the valve casing on the outer periphery of the outer peripheral valve seat plate portion is formed.

  According to the present invention, it is possible to provide a refrigerant switching valve with high assembly accuracy and improved reliability, and a device using the refrigerant switching valve.

It is the front external view which looked at the refrigerator of 1st Embodiment from the front. It is EE sectional drawing of FIG. 1 showing the structure in the store | warehouse | chamber of a refrigerator. It is a front view showing the functional structure in the refrigerator compartment. FIG. 3 is an enlarged explanatory view of a main part showing the vicinity of the cooler in FIG. 2 in an enlarged manner. It is a figure which shows the 1st mode of the refrigerant | coolant path | route using the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a figure which shows the 2nd mode of the refrigerant | coolant path | route using the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a figure which shows the 3rd mode of the refrigerant | coolant path | route using the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a figure which shows the 4th mode of the refrigerant | coolant path | route using the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a perspective view which shows the external appearance of the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a G direction arrow line view of FIG. It is FF sectional drawing of FIG. It is the perspective view which shows the internal structure of a refrigerant | coolant switching valve, and is the perspective view which removed virtually the stator case and the valve case from the refrigerant | coolant switching valve, and was seen through. It is a perspective view which shows the structure of a rotor pinion gear, an idler gear, and a valve body. It is explanatory drawing which shows arrangement | positioning of the communicating port of the refrigerant | coolant switching valve which concerns on 1st Embodiment, and the shape of a valve body sliding contact surface. It is explanatory drawing which shows rotation and the open / close state of the valve body of the refrigerant | coolant switching valve which concerns on 1st Embodiment. It is a figure explaining the internal structure of the refrigerant | coolant switching valve from the 1st state at the time of switching the refrigerant | coolant switching valve which concerns on 1st Embodiment, and a 4th state, and a refrigerant | coolant path | route. It is an expanded partial sectional view which shows the cross section of the 2nd valve seat plate part of a refrigerant | coolant switching valve, a valve body, and a communicating pipe. It is FF sectional drawing which shows the state which brazed the refrigerant | coolant inflow pipe, the refrigerant | coolant outflow pipe, and the idler axis | shaft to the valve seat plate of a refrigerant | coolant switching valve. It is a perspective view which shows the state which brazed the refrigerant | coolant inflow pipe | tube, the refrigerant | coolant outflow pipe, and the idler axis | shaft to the valve seat plate of a refrigerant | coolant switching valve. It is a figure which shows the state which expanded and temporarily fixed some refrigerant | coolant inflow pipes to the valve seat plate. It is sectional drawing of the valve seat plate of a refrigerant | coolant switching valve. It is sectional drawing which shows the positional relationship of the outermost peripheral part of a valve seat plate, and a valve case. It is a figure which shows the internal structure of the refrigerant | coolant switching valve from the 1st state of the refrigerant | coolant switching valve which concerns on 2nd Embodiment to a 3rd state. It is a perspective view which shows the shape of the valve body of the refrigerant | coolant switching valve which concerns on 2nd Embodiment. It is a figure which shows the internal structure of the refrigerant | coolant switching valve from the 1st state of a refrigerant | coolant switching valve which concerns on 3rd Embodiment to a 4th state. It is a figure which shows the internal structure of the refrigerant | coolant switching valve from the 1st state of a refrigerant | coolant switching valve which concerns on 4th Embodiment to a 2nd state. It is an expanded fragmentary sectional view which shows the cross section of the valve seat plate of the refrigerant | coolant switching valve when the pressure by the side of a communicating pipe rises, a valve body, and a communicating pipe. It is sectional drawing which shows the structure of the valve seat plate of the refrigerant | coolant switching valve which concerns on 5th Embodiment.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, embodiments that are modes for carrying out the invention will be described with reference to the accompanying drawings. In addition, in each figure, the same code | symbol is attached | subjected and shown to the same part, and the overlapping description is abbreviate | omitted.

<< First Embodiment >>
FIG. 1 is a front external view of the refrigerator according to the first embodiment as viewed from the front. FIG. 2 is a cross-sectional view taken along the line EE of FIG. FIG. 3 is a front view illustrating a functional configuration in the refrigerator. FIG. 4 is an enlarged explanatory view of a main part showing the vicinity of the cooler of FIG. 2 in an enlarged manner.
<Configuration of equipment (refrigerator 1) using refrigerant switching valve 60>
Before describing the refrigerant switching valve 60 (see FIG. 9 and the like) according to the first embodiment, first, as an apparatus including the refrigerant switching valve 60 (see FIG. 9 and the like), the refrigerator 1 is taken as an example, and FIG. 4 will be described.

  As shown in FIG. 1 and FIG. 3, the refrigerator 1 has a refrigerator main body 1 </ b> H as its main body, from above, a refrigerator compartment 2, an ice making room 3 and an upper freezer compartment 4 arranged on the left and right, a lower freezer compartment 5, A vegetable room 6 is provided. In addition, the refrigerator compartment 2 and the vegetable compartment 6 are storage rooms of a refrigerator temperature zone, for example, are made into the temperature of about 3-5 degreeC. Further, the ice making room 3, the upper freezing room 4, and the lower freezing room 5 are storage rooms in a freezing temperature zone, and have a temperature of about -18 ° C, for example.

  As shown in FIG. 1, the refrigerating room 2 includes, on the front side, refrigerating room doors 2a and 2b having a double door (so-called French type) divided into left and right sides. In addition, the ice making chamber 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are each provided with a drawer type ice making door 3a, an upper freezer compartment door 4a, a lower freezer compartment door 5a, and a vegetable compartment door 6a. . In the following description, the refrigerator compartment doors 2a, 2b, the ice making compartment door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are simply referred to as the doors 2a, 2b, 3a, 4a, 5a, 6a. May be called.

  The doors 2a, 2b, 3a, 4a, 5a, and 6a are provided with rubber door packings 15 (see FIG. 2) around the inside. The door packing 15 is elastically deformed when the doors 2a, 2b, 3a, 4a, 5a, and 6a are closed, and is brought into close contact with the opening peripheral edge 1H2 of the front surface 16 of the refrigerator main body, so 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6) are closed and sealed with respect to the external space to suppress the leakage of cold air from the storage space to the outside.

  The refrigerator 1 has a door sensor (not shown) for detecting the open / closed state of the doors 2a, 2b, 3a, 4a, 5a, 6a and doors 2a, 2b as door opening / closing detection / notification means. An alarm (not shown) that informs the user with a notification sound when a state in which it is determined that 3a, 4a, 5a, and 6a are open is continued for a predetermined time (for example, 1 minute or more). Have.

  In addition, the refrigerator 1 has a temperature setting device for the user to set the temperature of the refrigerator compartment 2 and the temperature of the upper freezer compartment 4 and the lower freezer compartment 5. The temperature setting device is the control panel 40 shown in FIG. 1 having an operation unit and a display unit.

  As shown in FIG. 2, the refrigerator main body 1H is formed by filling the outside of the refrigerator and the inside of the refrigerator with a foam insulation (foamed polyurethane) between the resin inner box 10a and the steel plate outer box 10b. The heat insulating box 10 is insulated and separated. Moreover, in order to improve the heat insulation performance, the heat insulation box 10 of the refrigerator main body 1H is mounted with a plurality of vacuum heat insulating materials 14 having a lower heat transfer coefficient along the inner surface of the outer box 10b.

  In the refrigerator 1, a plurality of storage chambers arranged in different vertical directions with different temperature zones of the refrigeration temperature zone and the freezing temperature zone are partitioned by heat insulation partition walls 11 a and 11 b in order to suppress heat leakage. Has been.

  That is, by the upper heat insulating partition wall 11a, the refrigerating room 2 which is a refrigerating temperature zone storage room, the upper freezing room 4 and the ice making room 3 which are refrigerating temperature zone storage rooms (see FIG. 1, the ice making room 3 in FIG. 2). (Not shown) are insulated from each other. In addition, the lower heat insulating partition wall 11b insulates the lower freezing room 5 that is a storage room in a freezing temperature zone and the vegetable room 6 that is a storage room in a refrigerating temperature zone.

  As shown in FIG. 2, a plurality of door pockets 13 for storing (storing) drinks and the like are provided on the inner side of the refrigerator compartment doors 2a and 2b so as to protrude toward the inner side. The refrigerator compartment 2 is partitioned into a plurality of storage spaces in the vertical direction by a plurality of shelves 12 on which food or the like is placed.

  The ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 having a drawer-type door are housed integrally behind each door 3a, 4a, 5a, 6a provided in front of each storage room. Containers 3b, 4b, 5b, 6b are respectively provided. The storage containers 3b, 4b, 5b, and 6b can be pulled out by placing a hand on a handle portion (not shown) of the doors 3a, 4a, 5a, and 6a and pulling it out to the front side.

<Condensation prevention>
Here, if each door 2a, 2b, 3a, 4a, 5a, 6a of the refrigerator main body 1H is opened, warm outside air will contact with the opening peripheral part 1H2 of the front surface 16 of the refrigerator main body. In particular, since the inside of the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 is a freezing temperature zone below freezing (for example, −18 ° C.), when the doors 3a, 4a, and 5a are opened, the opening of the front surface 16 of the refrigerator body is opened. When the outside air touches the peripheral edge portion 1H2 and is cooled, the dew point or lower is reached, and moisture in the outside air is likely to condense on the front surface 16 of the refrigerator body.

  Furthermore, if the doors 3a, 4a, and 5a are closed in a state of condensation on the refrigerator main body front surface 16, water droplets between the door packing 15 and the refrigerator main body front surface 16 may be cooled below freezing point and may freeze.

  Therefore, as shown in FIGS. 2 and 3, the opening periphery 1H2 of the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 is heated to increase the dew point temperature in order to prevent condensation. A refrigerant pipe 17 that allows passage of a high-temperature refrigerant after passing through a condenser 52 described later is embedded. Here, the temperature of the refrigerant flowing through the refrigerant pipe 17 (the temperature of the refrigerant after passing through the condenser 52 described later) is higher than the outside temperature (the temperature of the external space). For example, the outside temperature is 30. The temperature is set to about 33 ° C.

  Thus, the refrigerant | coolant piping 17 has a function which heats the opening peripheral part 1H2 of the refrigerator main body front surface 16 with the heat | fever of the flowing refrigerant | coolant, and suppresses the dew condensation and freezing of the water | moisture content in external air. In the following description, the refrigerant pipe 17 is referred to as “condensation prevention pipe 17”.

  In addition, in this 1st Embodiment, although it was set as the structure which provided the dew condensation prevention piping 17 in the opening peripheral part 1H2 of the ice making chamber 3, the upper stage freezing room 4, and the lower stage freezing room 5, opening 1H2 of the refrigerator compartment 2 and the vegetable compartment 6 In this case, the effect of preventing condensation can be obtained.

<Cooling air circulation>
As shown in FIG. 2 and FIG. 3, the cooler 7 is disposed in a cooler storage chamber 8 provided almost on the back side of the lower freezing chamber 5. The cooler 7 is configured by attaching a large number of fins for expanding the heat transfer area to the cooler pipe 7d, and heat exchange between the refrigerant in the cooler pipe 7d and the air is performed.

  Further, an internal fan 9 (for example, a fan driven by a motor) is provided above the cooler 7. The air cooled by the heat exchange by the cooler 7 (hereinafter, the low-temperature air heat-exchanged by the cooler 7 is referred to as “cold air”) is sent by the internal fan 9 to the refrigerator compartment air duct 22 and the vegetable compartment air duct. 25, storage rooms of the refrigerator compartment 2, the vegetable compartment 6, the ice making chamber 3, the upper freezer compartment 4 and the lower freezer compartment 5 through the ice making compartment air duct 26a, the upper freezer compartment air duct 26b and the lower freezer compartment air duct 27 Sent to. Incidentally, each of the air ducts (22, 26a, 26b, 27, 25) to the refrigerator compartment 2, the ice making chamber 3, the upper freezer compartment 4, the lower freezer compartment 5 and the vegetable compartment 6 is a refrigerator main body as shown in FIG. It is provided on the back side of each 1H storage room.

  The blower support part 30 to which the internal blower 9 is attached partitions the cooler storage chamber 8 and the freezing temperature zone back partition 29.

  As shown in FIG. 4, the freezing temperature zone back partition 29 in which the air outlets 3 c, 4 c, and 5 c for blowing cold air to the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are formed is the upper freezing chamber 4. The ice making chamber 3 and the lower freezing chamber 5 are separated from the cooler storage chamber 8.

  The blower cover 31 is disposed so as to cover the front surface of the internal fan 9. Between the blower cover 31 and the freezing temperature zone back partition 29, an ice making chamber blow duct 26a and an upper freezer compartment blow duct for guiding the cool air blown by the internal blower 9 to the outlets 3c, 4c, 5c. 26b and a lower stage freezer compartment air duct 27 are formed.

  Moreover, the blower outlet 31a is formed in the upper part of the air blower cover 31, and the freezing temperature zone room cool air control means 21 is provided near the blower outlet 31a.

  Further, the blower cover 31 also plays a role of blowing cold air blown by the internal fan 9 toward the refrigeration temperature zone cold air control means 20 side. That is, the cold air that does not flow to the refrigeration temperature zone cold air control means 21 side provided in the blower cover 31 passes to the refrigeration temperature zone room cold air control means 20 side via the cold room upstream duct 23 as shown in FIG. Led.

  The blower cover 31 includes a rectifying unit 31 b on the front surface of the internal fan 9. The rectifying unit 31b rectifies the turbulent flow caused by the cold air blown out to prevent noise generation.

<Damper>
The storage room to which the cool air from the cooler 7 is sent is controlled by opening and closing the refrigeration temperature zone cool air control means 20 and the freezing temperature zone room cool air control means 21 shown in FIGS.

  Here, the refrigeration temperature chamber cold air control means 20 is a so-called twin damper having two independent first and second openings 20a and 20b (see FIG. 3), and opens and closes the first opening 20a. Therefore, the ventilation to the refrigerator compartment ventilation duct 22 is controlled, and the ventilation to the vegetable compartment ventilation duct 25 is controlled by opening and closing the second opening 20b.

  As shown in FIG. 4, the refrigeration temperature chamber cool air control means 21 is a single damper having a single opening, and by opening and closing the opening, an ice making room air duct 26a, an upper stage freezer room air duct 26b, and The ventilation to the lower freezer compartment ventilation duct 27 is controlled.

<Cooling the refrigerator compartment 2 with a damper>
When the refrigerator compartment 2 is cooled, if the first opening 20a of the refrigerator temperature zone cool air control means 20 is opened, the cool air passes through the refrigerator compartment upstream duct 23 (see FIG. 4) and the refrigerator compartment air duct 22; It is sent to the refrigerator compartment 2 from the outlet 2c (refer FIG. 3) provided in multiple stages. And the cold air which cooled the refrigerator compartment 2 flows into the cooler storage chamber 8 from the side lower part through the refrigerator outlet return duct 24 from the return port 2d provided in the lower part of the refrigerator compartment 2, and the cooler 7 Heat exchanged with it.

<Cooling the vegetable compartment 6 with a damper>
When the vegetable room 6 is cooled, if the second opening 20b of the refrigeration temperature zone cold air control means 20 is opened, the cold air passes through the cold room upstream duct 23 and the vegetable room air duct 25 (see FIG. 3), It is sent to the vegetable compartment 6 from the blower outlet 6c (refer FIG. 3). And the cold air which cooled the vegetable compartment 6 flows into the cooler storage chamber 8 from the lower part through the return port 6d, is heat-exchanged with the cooler 7, and is cooled.

  By the way, the amount of air circulating through the vegetable compartment 6 is less than the amount of air circulating through the refrigerator compartment 2 or the freezing temperature zone (3, 4, 5) because the refrigerator temperature is slightly higher than that of the refrigerator compartment 2. It has become.

<Cooling the freezer compartment (3, 4, 5) with a damper>
When cooling the freezer compartment (3, 4, 5), if the freezing temperature zone cold air control means 21 is opened, the cold air passes through the ice-making room air duct 26a and the upper freezer room air duct 26b, and the outlet 3c, 4c is sent to the ice making chamber 3 and the upper freezing chamber 4, respectively. Further, the cold air is sent to the lower freezer compartment 5 from the outlet 5c through the lower freezer compartment air duct 27 (see FIG. 2). In this way, the freezing temperature zone cold air control means 21 is attached above the blower cover 31 (see FIG. 4) and facilitates air blowing to the freezing chambers (3, 4, 5) disposed below the fan cover 31. Yes.

  The cold air blown to the ice making chamber 3 through the ice making chamber air duct 26a and the cold air blown to the upper freezer chamber 4 through the upper freezer chamber air duct 26b descend to the lower freezer chamber 5 disposed below. To do. Then, together with the cool air blown to the lower freezer compartment 5 through the lower freezer compartment air duct 27, the inside of the cooler storage chamber 8 through the freezer return port 28 provided in the lower part of the lower freezer compartment 5 is provided. It flows in and is heat-exchanged with the cooler 7 to be cooled.

  Incidentally, the width dimension of the freezer compartment return port 28 is substantially equal to the width dimension of the cooler 7.

  By the way, when the refrigeration temperature zone cold air control means 20 and the freezing temperature zone cold air control means 21 are in the open state, most of the cold air is sent to the freezing temperature zone cold air control means 21 side, and the remaining other cold air is discharged. Each air duct and the like are configured to be led to the refrigeration temperature zone cold air control means 20 side. Accordingly, one cooler is provided for the freezing temperature zone (ice making chamber 3, upper freezing chamber 4 and lower freezing chamber 5) and the refrigerating temperature zone (refrigeration room 2 and vegetable room 6) which are storage rooms having different temperature zones. 7 can supply cold air.

  As described above, switching of the cool air to be blown to each storage chamber of the refrigerator main body 1H is performed by appropriately opening and closing the refrigeration temperature zone cool air control means 20 and the freezing temperature zone room cool air control means 21.

<Defrost heater 35 of defrosting device>
As shown in FIG. 4, a defrost heater 35, which is a defrosting unit, is installed below the cooler 7. An upper cover 36 is provided above the defrost heater 35 in order to prevent defrost water from dripping onto the defrost heater 35.

  The defrost water generated by the defrosting (melting) of the frost attached to the walls of the cooler 7 and the surrounding cooler storage chamber 8 flows into the trough 32 provided at the lower part of the cooler storage chamber 8. It reaches the evaporating dish 34 disposed in the machine room 50 via the drain pipe 33 and is stored, evaporated by heat generated by the compressor 51 (see FIG. 3) and the condenser 52 described later, Discharged.

<Machine room>
As shown in FIG. 3, a machine room 50 is provided on the lower back surface (back) side of the heat insulating box 10.

  The machine room 50 includes a compressor 51 that compresses and discharges the refrigerant at a high temperature and high pressure, a condenser 52 that exchanges heat between the refrigerant and air, and a warehouse that promotes heat exchange between the refrigerant and air in the condenser 52. An outer blower 53, a decompression means 54 that is a thin tube, and a refrigerant switching valve 60 are arranged.

  The compressor 51, the condenser 52, the decompression means 54, and the refrigerant switching valve 60 are connected to the cooler 7 and the dew condensation prevention pipe 17 through a pipe, and a refrigerant path (refrigerant circuit) through which the refrigerant flows (from FIG. 5). As will be described later with reference to FIG.

<Sensor and control system>
As shown in FIG. 2, on the upper side of the ceiling wall 1H1 of the refrigerator main body 1H, as a control means, a memory such as a CPU (Central Processing Unit), a ROM (Read Only Memory), a RAM (Random Access Memory), etc. A control board 41 which is a control means on which a microcomputer, an interface circuit and the like are mounted is arranged.

  The refrigerator 1 includes an outside air temperature sensor 42 that detects a temperature environment outside the warehouse (outside air temperature), an outside air humidity sensor 43 that detects a humidity environment outside the warehouse (outside air humidity) using, for example, a moisture adsorption solid electrolyte, and refrigeration. Refrigeration room temperature sensor 44 for detecting the temperature of the room 2, vegetable room temperature sensor 45 for detecting the temperature of the vegetable room 6, and the temperatures of the freezing temperature zones (the ice making room 3, the upper freezing room 4 and the lower freezing room 5) Temperature sensors such as a freezer temperature sensor 46 that performs cooling and a cooler temperature sensor 47 that detects the temperature of the cooler 7 are provided. The temperature detected by these sensors is input to the control board 41 as a detection signal.

  The control board 41 includes a door sensor (not shown) for detecting the open / closed state of the doors 2a, 2b, 3a, 4a, 5a, 6a, and a control panel 40 (see FIG. 1) provided on the refrigerator compartment door 2a. Electrically connected.

  Then, the control board 41 executes a control program pre-installed in the ROM, thereby controlling the ON / OFF of the compressor 51 and the rotational speed, the refrigeration temperature zone cool air control means 20 and the freezing temperature zone cool air control. Control of each driving motor (not shown) for individually opening and closing the means 21, ON / OFF of the internal fan 9 and control of the rotational speed, ON / OFF of the external fan 53 (see FIG. 3) and rotational speed And the like, control of ON / OFF of an alarm (not shown) for notifying the door open state, switching operation of the refrigerant switching valve 60, and the like, and overall operation of the refrigerator 1 is controlled.

  The above is the structure of the refrigerator 1 which is an apparatus.

<Refrigerant path (refrigerant circuit)>
Next, the refrigerant | coolant path | route (refrigerant circuit) of the refrigerator 1 provided with the refrigerant | coolant switching valve 60 (refer FIG. 3, FIG. 9, etc.) which concerns on 1st Embodiment, and an operation mode are demonstrated using FIGS.

  FIG. 5 is a diagram illustrating a first mode of the refrigerant path using the refrigerant switching valve 60 according to the first embodiment. FIG. 6 is a diagram illustrating a second mode of the refrigerant path using the refrigerant switching valve 60 according to the first embodiment. FIG. 7 is a diagram illustrating a third mode of the refrigerant path using the refrigerant switching valve 60 according to the first embodiment. FIG. 8 is a diagram illustrating a fourth mode of the refrigerant path using the refrigerant switching valve 60 according to the first embodiment.

  The first mode in FIG. 5 is a normal mode, which is a dew condensation prevention mode in which high-temperature refrigerant is sent to the dew condensation prevention pipe 17 (see FIGS. 2 and 3) to suppress dew condensation.

  The second mode in FIG. 6 is a bypass mode in which the refrigerant bypasses the condensation prevention pipe 17 in an environment where there is no possibility of condensation.

  The third mode in FIG. 7 is a stop mode in which the compressor 51 is stopped.

  The fourth mode in FIG. 8 is a refrigerant recovery mode in which the refrigerant is recovered from the dew condensation prevention pipe 17 to save energy.

  The refrigerant switching valve 60 is connected to four communication pipes (an inflow pipe 68, communication pipes 69b, 69c, and 69d, which will be described later with reference to FIG. 9 and the like), and includes one inflow port A, three communication ports B, It is a so-called four-way valve provided with C and D.

  That is, the inflow pipe 68 is connected to the inflow port A, and the communication pipes 69b, 69c, and 69d are connected to the three communication ports B, C, and D, respectively.

  As shown in FIG. 5, a first refrigerant pipe 55 is connected to the upstream side of the inflow port A. The first refrigerant pipe 55 is connected to the condenser 52 on the upstream side, and further connected to the high-pressure side discharge port 51o of the compressor 51 on the upstream side. One end of the second refrigerant pipe 56 is connected to the communication port B, and the other end of the second refrigerant pipe 56 is connected to the communication port D via the condensation prevention pipe 17. A third refrigerant pipe 57 is connected to the downstream side of the communication port C.

The third refrigerant pipe 57 is connected to the cooler 7 via the pressure reducing means 54 that is a downstream narrow pipe. The downstream side of the cooler 7 is connected to the low-pressure side suction port 51 i of the compressor 51. Incidentally, as a refrigerant in the refrigerant path (refrigerant circuit), for example, isobutane that emits less CO ₂ during processing can be used.

  Since the first mode to the fourth mode shown in FIGS. 5 to 8 are different in mode, the open / close state (communication state) of the refrigerant switching valve 60 is different, and the refrigerant path (circuit) is different.

(First Mode in FIG. 5) Condensation Prevention Mode In the first mode (condensation prevention mode) shown in FIG. 5, the refrigerant switching valve 60 communicates with the inlet A and the communication port B (refrigerant flow L1). The port C communicates with the communication port D (refrigerant flow L2).

  The high-temperature and high-pressure refrigerant compressed by the compressor 51 flows into the condenser 52 and is cooled by exchanging heat with air (external air). The refrigerant flowing out of the condenser 52 flows into the inlet A of the refrigerant switching valve 60 through the first refrigerant pipe 55, and flows out of the communication port B as indicated by the refrigerant flow L1. Then, it flows into the dew condensation prevention pipe 17 through the second refrigerant pipe 56.

  Since the temperature of the refrigerant that has flowed into the dew condensation prevention pipe 17 (that is, the temperature of the refrigerant that has flowed out of the condenser 52) is higher than that of the outside air, the refrigerant that has flowed into the dew condensation prevention pipe 17 is opened in the refrigerator main body 1H. The peripheral edge 1H2 (see FIGS. 2 and 3) is heated. Thereby, the temperature of the opening peripheral part 1H2 of the refrigerator main body 1H rises, the dew point temperature rises, and dew condensation is suppressed.

  The refrigerant that radiates heat to the opening peripheral edge 1H2 and has a temperature lower than that at the time of flowing into the dew condensation prevention pipe 17 flows out of the dew condensation prevention pipe 17, passes through the downstream side of the second refrigerant pipe 56, and switches the refrigerant. It flows into the communication port D of the valve 60. Then, as shown in the refrigerant flow L2, the refrigerant flows out from the communication port C, passes through the third refrigerant pipe 57, passes through the decompression means 54 that is a thin tube, and then adiabatically expands to become a low temperature and low pressure.

  The refrigerant after passing through the decompression means 54 flows into the cooler 7 (cooler pipe 7d) (see FIG. 4) which is an evaporator. The low-temperature refrigerant that has flowed into the cooler 7 (cooler pipe 7 d) evaporates by exchanging heat with ambient air in the cooler 7 and returns to the compressor 51.

  Thus, in the first mode (condensation prevention mode), the refrigerant temperature passing through the condensation prevention pipe 17 is higher than the outside air temperature where the refrigerator main body 1H is installed, so even if the outside air is hot and humid. And the temperature of the opening peripheral part 1H2 of the refrigerator main body 1H rises, and the dew condensation of the opening peripheral part 1H2 of the refrigerator main body 1H can be suppressed.

(Second Mode in FIG. 6) Bypass Mode As shown in FIG. 6, in the second mode (bypass mode), the refrigerant switching valve 60 communicates between the inlet A and the communication port C (refrigerant flow L3). The communication port B and the communication port D do not communicate with others.

  The high-temperature and high-pressure refrigerant compressed by the compressor 51 flows into the condenser 52 and is cooled by exchanging heat with air (external air) in the condenser 52. The refrigerant flowing out of the condenser 52 flows into the inlet A of the refrigerant switching valve 60 through the first refrigerant pipe 55, flows out of the communication port C as shown in the refrigerant flow L3, and flows into the third refrigerant pipe. After passing through the pressure reducing means 54 which is a thin tube through 57, it adiabatically expands to become a low temperature and low pressure and flows into the cooler 7 (cooler pipe 7d) which is an evaporator. The low-temperature refrigerant that has flowed into the cooler 7 (cooler pipe 7d) (see FIG. 2) evaporates by exchanging heat with ambient air in the cooler 7, and returns to the compressor 51.

  When operating in the first mode (condensation prevention mode) (see FIG. 5), a refrigerant having a temperature higher than that of the outside air flows through the dew condensation prevention pipe 17, so that storage room (the ice making room 3, the upper freezer room 4, the lower freezer room) 5) There is a risk of warming (see FIG. 3) and the like. Therefore, when the risk of condensation is low, such as when the outside air is low humidity, the refrigerant can be prevented from flowing through the condensation prevention pipe 17 by operating in the second mode (bypass mode).

  Thereby, although there is no effect of preventing condensation on the opening peripheral edge 1H2 of the refrigerator body 1H, when the possibility of condensation is low, heat leakage from the condensation prevention pipe 17 to the inside of the refrigerator body 1H can be prevented. Energy saving performance can be improved.

  In the first mode (condensation prevention mode) and the second mode (bypass mode) of the refrigerant switching valve 60, there is a risk of condensation based on the detection results of the outside air temperature sensor 42 and the outside air humidity sensor 43 shown in FIG. Determine.

  For example, the dew point is obtained from the humidity of the outside air detected by the outside air humidity sensor 43, and whether or not the environment is likely to condense is obtained from the outside air temperature detected by the outside air temperature sensor 42. Alternatively, the saturation humidity is obtained from the outside air temperature detected by the outside air temperature sensor 42, and whether or not the environment is likely to condense is obtained from the humidity of the outside air detected by the outside air humidity sensor 43.

  When there is a possibility of condensation, the mode is switched to the first mode (condensation prevention mode), and when there is no risk of condensation, the mode is switched to the second mode (bypass mode). Condensation can be prevented, and heat leakage can be suppressed at other times, that is, when condensation is not likely to occur, which is effective in reducing power consumption.

(Third mode in FIG. 7) Stop mode In the third mode (stop mode) shown in FIG. 7, the compressor 51 is in a stopped state, and the refrigerant switching valve 60 closes the communication port C. .

  In the third mode, the communication port C is closed to block the circuit through which the refrigerant circulates. That is, since the communication port C of the refrigerant switching valve 60 is blocked, the relatively high-temperature refrigerant in the first refrigerant pipe 55, the condenser 52, the second refrigerant pipe 56, and the refrigerant dew condensation prevention pipe 17 is The flow into the refrigerant pipe 57 and the cooler 7 is blocked. Thereby, the temperature rise of the cooler 7 can be prevented.

  Here, in the operation of cooling the storage room (2, 3, 4, 5, 6) by the refrigeration cycle, the refrigerator 1 operates the compressor 51 until the storage room becomes a predetermined temperature or less, and the storage room is The compressor 51 is stopped when the temperature falls below a predetermined temperature. When the storage chamber rises above a predetermined temperature, the compressor 51 is restarted to cool the storage chamber.

  By setting the refrigerant switching valve 60 to the third mode (stop mode) when the compressor 51 is stopped, the refrigerant in the cooler 7 can be maintained at a low temperature. Therefore, when the compressor 51 is restarted, the refrigerant in the cooler 7 is at a low temperature, so that the heat exchange efficiency is high and the energy saving performance of the refrigerator 1 can be improved.

(Fourth Mode in FIG. 8) Refrigerant Recovery Mode As shown in FIG. 8, in the fourth mode (refrigerant recovery mode), the refrigerant switching valve 60 blocks the inlet A and the communication port D so as not to communicate with others. The communication port B and the communication port C communicate with each other, and the refrigerant flows like a refrigerant flow L4.

  Since the inflow port A does not communicate with any of the communication ports B, C, and D, the refrigerant does not flow even when the compressor 51 is operated, and the condenser 52 on the downstream side of the high-pressure side discharge side 51o of the compressor 51. The first refrigerant pipe 55 communicates with the high-pressure side discharge port 51o of the compressor 51 and enters a high-pressure state.

  On the other hand, since the communication port B and the communication port C communicate with each other, the second refrigerant pipe 56 and the third refrigerant pipe 57 communicate with each other. Since the communication port D is closed, the refrigerant does not flow even when the compressor 51 is operated, and the second refrigerant pipe 56 and the dew condensation prevention pipe 17 on the downstream side of the communication port D and the downstream side of the communication port C. The third refrigerant pipe 57 connected to the suction side of the compressor 51, the decompression means 54, which is a narrow pipe, and the cooler 7 have the same low pressure as the low pressure side suction port 51 i of the compressor 51 due to the operation of the compressor 51. It becomes a state.

  That is, when the compressor 51 is operated in the fourth mode (refrigerant recovery mode), the refrigerant in the second refrigerant pipe 56 and the dew condensation prevention pipe 17 is sucked into the cooler 7 by the low pressure of the low-pressure side inlet 51 i of the compressor 51. can do. When the compressor 51 is restarted, the amount of refrigerant in the second refrigerant pipe 56 and the dew condensation prevention pipe 17 is small, while there is sufficient refrigerant in the cooler 7 and the heat exchange efficiency is high. The energy saving performance of the refrigerator 1 can be improved.

  The above is the refrigerant circuit of the refrigerator 1 and the operation modes of the first to fourth modes.

<< Refrigerant switching valve 60 >> (arrangement of communication ports B, C, D)
Next, the configuration and operation of the refrigerant switching valve 60 according to the first embodiment will be described with reference to FIGS. 9 to 16.

  FIG. 9 is a perspective view showing an appearance of the refrigerant switching valve 60 according to the first embodiment. 10 is a view in the direction of the arrow G in FIG. 11 is a cross-sectional view taken along line FF in FIG. FIG. 12 is a perspective view showing the internal configuration of the refrigerant switching valve 60, and is a perspective view of the refrigerant switching valve 60 seen through virtually removing the stator case 61 and the valve case 66. FIG. 13 is a perspective view showing the configuration of the rotor pinion gear 75, the idler gear 79 and the valve body 80, and shows the configuration of the driving force transmission means using gears from the rotor 70 to the valve body 80.

  As shown in FIGS. 9 and 11, a substantially cylindrical stator 62 that is a stator of a motor around which a coil is wound is formed inside a substantially cylindrical stator case 61 that forms the exterior of the refrigerant switching valve 60. ing. Further, a connector case 63 projecting outwardly is formed in a part of the stator case 61, and the wiring from the coil of the stator 62 is connected to an external drive circuit in the connector case 63. A connector 65 having connector pins 64 is provided.

  The valve case 66 that covers the valve body 80 of the refrigerant switching valve 60 is integrally formed of, for example, a non-magnetic metal such as stainless steel by deep drawing, the upper end is closed, the lower end is opened, and the lower end is opened from the upper end side. It is formed in a bottomed cylindrical shape with a large diameter on the side, and the opened lower end is enlarged in a flange shape.

  As shown in FIG. 11, the upper side of the valve case 66 is fitted into the inner peripheral portion of the stator 62, while the lower side of the valve case 66 is an open end whose diameter is larger than that of the upper side. A disc-shaped valve seat plate 67 is fitted to the open end, and the entire periphery is sealed and joined by welding.

  As shown in FIGS. 10 to 12, the valve seat plate 67 is composed of three concentric portions having different thicknesses, and a disc-shaped first valve seat plate portion constituting a part of the valve seat plate 67. 67a and a disc shape that is smaller in diameter and thicker than the first valve seat plate portion 67a and protrudes in one direction toward the communication pipe 69 and encloses the center of the first valve seat plate portion 67a. A second valve seat plate portion 67b and a third valve seat plate portion (outer peripheral valve seat plate portion) that is thinner than the first valve seat plate portion 67a and constitutes the outermost outer shell of the valve seat plate 67 67c as a unit. Further, the surface of the valve seat plate 67 on the side in contact with the valve body 80 is preferably a polished finish surface 90. Details of the configuration of the valve seat plate 67 will be described later.

  As shown in FIGS. 11 to 12, one inflow pipe 68 is coupled to the first valve seat plate portion 67 a so as to seal the joint portion by brazing, and communicates with the inside of the valve case 66. Yes.

  As shown in FIGS. 10 to 12, the thickest second valve seat plate portion 67b includes three communication pipes 69b, a communication pipe 69c, and a communication pipe 69d, which are joined by brazing. It is connected so as to be sealed, and communicates with the inside of the valve case 66. As shown in FIGS. 10 and 11, the inflow pipe 68, the communication pipe 69b, the communication pipe 69c, and one end of the communication pipe 69d are respectively inflow ports opened toward the inside of the valve case 66 on one surface of the valve seat plate 67. A, a communication port B, a communication port C, and a communication port D are connected.

  A rotor 70 shown in FIG. 11 is a rotor of a motor having a magnet. When the connector pin 64 is connected to a drive circuit (not shown) and the coil of the stator 62 is energized, a magnetic field is generated in the stator 62, and the magnetic field is applied to the magnet of the rotor 70 via the valve case 66. Rotate around axis 71. An example of the configuration of this motor is a general stepping motor, and although detailed explanation is omitted, it rotates at a certain angle.

  The valve body shaft 71 is a rotation center axis of the rotor 70 and is an axis that becomes a rotation center of the valve body 80 described later.

  The first valve seat plate portion 67a or the second valve seat plate portion 67b is substantially stopped, and preferably, at the center position, a rotor shaft hole 72 that is a fitting hole for the valve body shaft 71 is a second valve seat plate portion. It is formed as a bottomed hole so as not to penetrate 67b. The first valve seat plate portion 67 a and the second valve seat plate portion 67 b are disposed coaxially with the rotor shaft hole 72.

  As shown in FIG. 11, a rotor bearing 73 that is a concave portion is formed in the approximate center of the bottom portion of the cylinder above the valve case 66. One end of the valve body shaft 71 is supported by being fitted into the rotor shaft hole 72, and the other end is fitted and supported by the rotor bearing 73.

  The valve body shaft 71 is press-fitted and fixed in a rotor shaft hole 72 at one end provided in the valve seat plate 67, and is assembled with a rotor bearing 73 at the other end by loose fitting. That is, the rotor shaft hole 72 at one end has a slightly smaller diameter than the valve body shaft 71, and the rotor bearing 73 at the other end has a slightly larger diameter than the valve body shaft 71.

  However, since the valve body shaft 71 is press-fitted and fixed integrally with the rotor shaft hole 72, even if the coaxiality between the rotor shaft hole 72 and the rotor bearing 73 is not highly accurate, the valve body shaft 71 can be It can be planted at right angles to the seat plate 67 with high accuracy. Thereby, the coaxiality of the valve seat plate 67 and the valve case 66, the valve case 66 and the rotor 70, and the rotor 70 and the stator 62 is improved. Therefore, the motor performance is improved.

(Inlet A, position of communication ports B, C, D of refrigerant switching valve 60)
As shown in FIG. 10, the communication port B, the communication port C, and the communication port D that are opened on the lower surface of the refrigerant switching valve 60 are arranged on the same circle around the valve body shaft 71 (rotor shaft hole 72). ing.

  Suitable arrangement angles of the communication port B, the communication port C, and the communication port D will be described in detail later.

  In the first embodiment, the communication port D is provided at a position close to the inflow port A with respect to the valve body shaft 71 (rotor shaft hole 72). The communication port B is provided on the opposite side of the communication port B across the valve body shaft 71 (rotor shaft hole 72).

  The communication port C has a relationship of approximately 90 ° with respect to the communication port B and the communication port D on the side of the valve body shaft 71 (rotor shaft hole 72), and is provided in the vicinity of the idler shaft 78. ing.

  The positions of the communication port B, the communication port C, and the communication port D are the positions of this example with respect to the inlet A or the idler shaft 78 as long as they satisfy the mutual arrangement relationship around the valve body shaft 71. It is not limited to relationships.

  As shown in FIGS. 10 and 12, in the first valve seat plate portion 67a, on the side close to the communication port C with respect to the valve body shaft 71 (rotor shaft hole 72), the rotation center of an idler gear 79 described later is provided. A fitting hole 78a of the idler shaft 78 is formed. One end of an idler shaft 78 is joined to the fitting hole 78a by sealing the joint to the first valve seat plate portion 67a by brazing.

  As shown in FIGS. 11, 12, and 13, the other end of the idler shaft 78 is not fixed, and the idler shaft 78 has a so-called cantilevered structure.

  The rotor 70 is integrally supported by the rotor drive unit 74, and the rotor 70 and the rotor drive unit 74 are rotated together with the valve body shaft 71 as a rotation center axis. As shown in FIG. 12, a rotor pinion gear 75 is formed below the rotor drive unit 74. That is, when the rotor 70 rotates, the rotor drive unit 74 and the rotor pinion gear 75 rotate together.

(Valve body sliding contact surface 81 of valve body 80)
The valve body 80 rotates around the valve body shaft 71 while contacting one surface of the valve body sliding contact surface 81 (see FIG. 13) with the polished surface 90 of the valve seat plate 67.

  The valve body 80 is configured to open and close communication ports B, C, and D (see FIG. 10) provided in the valve seat plate 67 by rotating.

  Further, a valve body sliding contact surface 81 (see FIG. 13) which is a surface in contact with the valve seat plate 67 of the valve body 80 is partially recessed so that two communicating ports can be selected as will be described later. A communication recess 82 (see FIG. 13) is provided. The relationship between the position of the communication recess 82 and the opening / closing operations of the communication ports B, C, and D will be described later. A valve body gear 83 is provided on the outer periphery of the valve body 80 on the side away from the valve seat plate 67 (see FIG. 11).

(Relationship between rotor pinion gear 75 and valve body 80)
The rotor pinion gear 75 formed integrally with the rotor drive unit 74 has a rotor drive unit tip 76, which is a convex portion provided around the rotation shaft at the lower end of the rotor pinion gear 75, placed on the upper surface of the valve body 80. . The rotor pinion gear 75 and the valve body 80 are rotatably arranged around a valve body shaft 71 that is a common central axis via a rotor drive shaft hole 77 and a valve body shaft hole 85, respectively.

(Pressing of valve body 80)
As shown in FIGS. 11 and 12, a rotor drive unit in which a leaf spring 86, which is a biasing means with a part of the arm extending radially toward the upper surface inside the valve case 66, supports the rotor 70 and rotates integrally therewith. 74 is disposed on the upper surface.

  As shown in FIG. 12, the reaction force in the direction of the valve body shaft 71 received by the arm of the leaf spring 86 from the inside of the upper surface of the valve case 66 is applied to the valve body 80 via the rotor drive unit 74 and the rotor pinion gear 75. Is pressed against the valve seat plate 67. Further, the weight of the rotor 70 is also added to the valve body 80.

  Here, as shown in FIG. 13, the position where the rotor driving unit tip 76 contacts the valve body 80 is in the vicinity of the valve body shaft 71, so the valve body 80 is in the vicinity of the rotating shaft (valve body shaft 71), That is, it is pressed in the axial direction against the valve seat plate 67 in the vicinity of the center of rotation, so that it is pressed uniformly and in a balanced manner.

(Idler gear 79)
As shown in FIGS. 11 and 12, an idler gear 79 having an idler large gear 79b and an idler pinion gear 79a is rotatably supported on the idler shaft 78. The idler large gear 79b meshes with the rotor pinion gear 75, and the idler pinion gear 79a meshes with the valve body gear 83 to decelerate. The rotational torque from the rotor 70 is transmitted while being decelerated in the order of the rotor pinion gear 75, the idler large gear 79b, the idler pinion gear 79a, and the valve body gear 83. The rotational torque from the rotor 70 increases as the valve body gear 83 is decelerated.

  Here, if the number of teeth of the rotor pinion gear 75 is Z1, the number of teeth of the idler large gear 79b is Z2, the number of teeth of the idler pinion gear 79a is Z3, and the number of teeth of the valve body gear 83 is Z4, all the gear modules are If they are the same, the distance between the shaft between the rotor pinion gear 75 and the idler large gear 79b and the distance between the shaft between the idler pinion gear 79a and the valve body gear 83 are equal if the relationship Z1 + Z2 = Z3 + Z4 is satisfied. The rotor pinion gear 75 and the valve body gear 83 can be arranged coaxially. For example, if Z1 = 12, Z2 = 34, Z3 = 13, Z4 = 33, then Z1 + Z2 = Z3 + Z4 = 46, and this relationship can be satisfied.

  Incidentally, the reduction ratio from the rotor 70 to the valve body 80 at this time is (Z1 × Z3) / (Z2 × Z4). In the above example, (12 × 13) / (34 × 33) = about 1 /7.2.

  From the relationship of (rotational torque) × (reduction ratio) = constant, the valve body 80 rotates at a torque 7.2 times the torque generated by the rotor 70. Therefore, there is a margin in the rotational torque of the valve body 80, and the switching operation of the valve body 80 can be reliably driven.

<Preferable Arrangement of Inflow Pipe 68, Second Valve Seat Plate 67b to Valve Body 80, and Idler Shaft 78 to Idler Gear 79>
Next, a preferred arrangement relationship among the inflow pipe 68, the second valve seat plate portion 67b or the valve body 80, and the idler shaft 78 or the idler gear 79 will be described with reference to FIGS.

  As shown in FIGS. 10 to 12, the inflow pipe 68 communicates with the inside of the valve case 66, and the refrigerant jets out from the inlet A into the valve case 66 at a high speed. When the refrigerant flows into the valve case 66 through the inflow pipe 68, the flow passage area is enlarged and the flow velocity is reduced, and the outlets B, C, which are opened according to the switching state of the valve body 80, It flows out from any of D to the communication pipe 69.

  Here, when the fluid force generated by the refrigerant jetted from the inlet A to which the inflow pipe 68 is connected acts on the idler gear 79, the idler gear 79 rises or vibrates, and the force acts on the valve body 80 meshed with the idler gear 79. The pressing force of the valve body 80 against the second valve seat plate portion 67b may change, and the sealing performance with respect to the second valve seat plate portion 67b may deteriorate.

  Therefore, in the first embodiment, the inlet A (inflow pipe 68) is provided on the other side of the outlet D with respect to the valve body 80 disposed coaxially with the valve body shaft 71 of the central axis of the valve case 66. The idler shaft 78 and the idler gear 79 are provided in the vicinity of the outlet C.

  Alternatively, the present invention is not limited to the first embodiment. An inlet A (inflow pipe 68) is provided on one side of the valve body 80, and an idler shaft 78 and an idler gear 79 are provided on the other side of the valve body 80. The structure to provide may be sufficient.

  With this arrangement, the idler gear 79 is not arranged in the vicinity of the inflow port A, so that the idler gear 79 is not subjected to the fluid force of the refrigerant flowing into the valve case 66, and the idler gear 79 does not float or vibrate. Therefore, since the pressing force of the valve body 80 against the valve seat plate 67 does not change, a stable sealing performance with respect to the valve seat plate 67 is obtained, and the highly reliable refrigerant switching valve 60 is obtained.

(Stopper 84 of valve body 80)
As shown in FIG. 13, a part of the valve body 80 is formed with a stopper 84 that is more convex than the outer periphery of the valve body gear 83. With this configuration, when the valve body 80 is rotated clockwise or counterclockwise by the maximum angle, the convex stopper 84 is formed on the cylindrical idler stopper 79c that protrudes below the idler pinion gear 79a of the idler gear 79. The rotation angle of the valve body gear 83 is limited to a predetermined angle range by contact.

  The rotation angle of the valve body gear 83 is a predetermined angle, for example, about 8 ° in addition to the rotation angle range necessary for the switching operation of the valve body 80 to be described later in order to secure a necessary rotation angle range. It is configured to stop the rotation by abutting after excessive rotation of the angle.

(Prevents falling off of cantilever idler gear 79)
As shown in FIG. 12, the idler gear 79 has a circumferential projection 79s formed on the upper surface of the idler large gear 79b. As shown in FIG. 11, the rotor driving unit 74 is formed with a protrusion 74 s in a circumferential shape. The idler shaft 78 of the idler gear 79 has a cantilever structure, but when the position of the idler gear 79 in the axial direction is shifted upward, the projection 79s of the idler gear 79 abuts on the projection 74s of the rotor drive unit 74. It cannot be moved any further. This prevents the idler gear 79 from falling off the cantilevered idler shaft 78.

<Operation of Refrigerant Switching Valve 60>
Next, opening / closing operations of the communication ports B, C, and D by the valve body 80 will be described with reference to FIGS.

  As the arrangement of the communication ports B, C, and D of the valve seat plate 67, the communication ports are arranged at three vertices in the virtual square 91, and the communication ports B, C, and D are opened and closed by the valve body 80. From the viewpoint of ease of rotation control of the valve body 80, it is more preferable.

  FIG. 14 is a diagram for explaining the positional relationship between the valve body sliding contact surface 81 of the valve body 80 and the communication ports B, C, and D in the first embodiment when viewed from the direction of arrow G in FIG. 14 to 16, the valve body sliding contact surface 81 that contacts the valve seat plate 67 is hatched for easy understanding.

(Rotation pitch of valve body 80)
In the adjacent communication ports B, C, and D, the angle formed by the center line connecting the communication ports B, C, and D and the valve body shaft 71 is 90 °.

  Here, the communication port B, the communication port C, and the communication port D are arranged adjacent to each other by 90 °, and the range from the communication port B to the communication port D is 180 °.

  If the valve body sliding contact surface 81 of the valve body 80 also covers the range of 180 °, the valve body 80 can simultaneously cover the communication ports B, C, and D. In the present embodiment, in addition, the communication recess 82 is provided on the valve body sliding contact surface 81 of the valve body 80 so as to communicate only within a range of 90 ° so that the communication port B and the communication port C communicate with each other. To place. That is, the communication ports B and C communicate with the communication recess 82, and the communication port D is covered with the valve body sliding contact surface 81.

  The valve body 80 is rotated counterclockwise from the angle 0 in the present embodiment, with the state shown in FIG.

  In this embodiment, it is assumed that it rotates 270 ° in the counterclockwise direction, and the open / close state of the communication ports B, C, D changes each time it rotates 90 ° in each direction.

  The open / closed states of the communication ports B, C, and D will be described with reference to FIG.

  FIG. 15 is an explanatory view showing the arrangement of the communication ports, the rotation of the valve body, and the open / closed state, which is the same as FIG.

15 shows that the valve body sliding contact surface 81 of the valve body 80 is counterclockwise around the valve body shaft 71.
(2) is the second state rotated 90 °,
(3) is the third state rotated 180 °,
(4) illustrates a fourth state rotated by 270 °.

  The valve body 80 is configured to rotate from the first state (1) to the fourth state (4) and reversibly rotate from the fourth state (4) to the first state (1). is there.

  FIG. 16 is a schematic diagram illustrating a refrigerant circuit when the refrigerant switching valve 60 is sequentially rotated by 90 ° from the first state of FIG. 15 (1) to the fourth state of (4). It is. In FIG. 16, both ends of the second refrigerant pipe 56 are connected to the communication port B and the communication port D, and the dew condensation prevention pipe 17 is provided between the communication port B and the communication port D. The communication port C is connected to the third refrigerant pipe 57.

  Here, as shown in FIG. 9, an inflow pipe 68 connected to the first refrigerant pipe 55 is fixed to the inflow port A.

  A communication pipe 69 b connected to one end of the second refrigerant pipe 56 is fixed to the communication port B.

  A communication pipe 69 c connected to the third refrigerant pipe 57 is fixed to the communication port C.

  A communication pipe 69 d connected to the other end of the second refrigerant pipe 56 is fixed to the communication port D.

<Refrigerant recovery mode>
The first state in FIG. 16A is the fourth mode shown in FIG. 8 and is the refrigerant recovery mode.

  In the first state (refrigerant recovery mode) of FIG. 16 (1), the communication port B and the communication port C communicate with each other by the communication recess 82, and the communication port D is closed by the valve body sliding contact surface 81.

  Since the communication port B, the communication port C, and the communication port D are all covered with the valve body 80, the refrigerant that has flowed into the valve case 66 from the inflow port A flows from the valve case 66 into the communication port B, the communication port C, and the communication port B. It does not flow to any of the communication ports D. Therefore, the refrigerant that has flowed into the valve case 66 from the inlet A cannot flow out of any of the communication ports B, C, and D, and the inlet A is closed.

  On the other hand, the second refrigerant pipe 56 and the third refrigerant pipe 57 are in communication with each other through the communication recess B at the communication port B and the communication port C. Therefore, if the compressor 51 is operated in this state, the second refrigerant pipe 56 and the dew condensation prevention pipe 17 on the downstream side of the communication port D are connected to the suction side of the compressor 51 from the downstream side of the communication port C. The third refrigerant pipe 57, the pressure reducing means 54, which is a thin pipe, and the cooler 7 are in a low pressure state that is equal to the low pressure side suction port 51i of the compressor 51, and the refrigerant is collected into the cooler 7 from the dew condensation prevention pipe 17 and the like. .

<Stop mode>
The second state in FIG. 16B is the third mode shown in FIG. 7 and is a stop mode in which the compressor 51 stops.

  In the second state of FIG. 16 (2), the inflow port A and the communication port D communicate with each other through the internal space of the valve case 66, and the communication ports C and B are closed. In this case, the compressor 51 is stopped and the refrigerant does not flow.

<Bypass mode>
The third state in FIG. 16 (3) is the second mode shown in FIG. 6 and is a bypass mode in which the refrigerant does not flow through the dew condensation prevention pipe 17.

  In the third state of FIG. 16 (3), the communication port B and the communication port D are closed.

  Since both ends of the second refrigerant pipe 56 connected to the communication ports B and D are closed, the refrigerant compressed by the compressor 51 and flowing from the inlet A of the refrigerant switching valve 60 through the condenser 52 is the valve case 66. It flows to the communication port C through the inside. The refrigerant passes from the communication port C through the third refrigerant pipe 57 and the decompression means 54 which is a thin tube, and then adiabatically expands to become low temperature and low pressure and flows into the cooler 7. The low-temperature refrigerant that has flowed into the cooler 7 (cooler pipe 7d) exchanges heat with the ambient air and returns to the compressor 51.

<Condensation prevention mode>
The fourth state in FIG. 16 (4) is the first mode shown in FIG. 5 and is a dew condensation prevention mode that is a normal mode in which the refrigerant flows through the dew condensation prevention pipe 17.

  In the fourth state of FIG. 16 (4), the communication port B is opened, and the communication port C and the communication port D are opened to the communication recess 82 and communicate with each other. The refrigerant that is compressed by the compressor 51 and flows from the inlet A of the refrigerant switching valve 60 through the condenser 52 flows out from the communication port B to the second refrigerant pipe 56 through the valve case 66 (see FIG. 11).

  The refrigerant flows into the communication recess 82 from the communication port D via the dew condensation prevention pipe 17, flows out of the communication port C, passes through the third refrigerant pipe 57, passes through the decompression means 54 that is a thin tube, and then adiabatically expands. The temperature becomes low temperature and low pressure and flows into the cooler 7. The low-temperature refrigerant that has flowed into the cooler 7 (cooler pipe 7d) exchanges heat with the ambient air and returns to the compressor 51.

  Here, in the present embodiment, a mode has been described in which the four modes of the refrigerant recovery mode, the stop mode, the bypass mode, and the dew condensation prevention mode can be switched, but without using the refrigerant recovery mode, A mode in which the three modes of the stop mode, the bypass mode, and the dew condensation prevention mode are switchable may be used. In the embodiment provided with such three modes, the valve body 80 can rotate only 180 ° from (2) the second state to (4) the fourth state in FIGS. 15 and 16. This can be realized by providing the stopper 84 at a position where the rotation angle of the valve body 80 is limited.

  Note that the angles of the communication ports B, C, and D around the valve body shaft 71 and the dimensions of the communication recess 82 are not particularly limited as long as the above four modes can be realized, and are not necessarily limited to the positional relationship.

≪Valve seat structure≫
Next, the valve seat structure of the refrigerant switching valve 60 according to the first embodiment will be further described with reference to FIGS.

FIG. 17 is an enlarged partial cross-sectional view showing a cross section of the second valve seat plate portion 67 b, the valve body 80, and the communication pipe 69 of the refrigerant switching valve 60.
FIG. 18 is an enlarged partial cross-sectional view showing the FF cross section in FIG. 10 of the valve seat plate 67, the communication pipe 69, the inflow pipe 68, and the idler shaft 78 of the refrigerant switching valve 60. FIG. 19 is an exploded perspective view virtually showing a state in which the valve body shaft 71 is press-fitted into the valve seat plate 67. 20 is an enlarged partial cross-sectional view showing the cross-sectional shapes of the first valve seat plate portion 67a and the inflow pipe 68. As shown in FIG. FIG. 21 is a sectional view similar to FIG. 18 showing the shape after polishing one surface of the valve seat plate. FIG. 22 is an enlarged partial cross-sectional view showing a cross section of the third valve seat plate portion 67 c and the valve case 66.

  As shown in FIG. 17, the second valve seat plate portion 67b is smaller in diameter than the outer peripheral first valve seat plate portion 67a, is integrally concentric, and is provided with a step.

  A bottomed rotor shaft hole 72 that does not penetrate from the side where the valve body 80 is disposed is formed in the center of the second valve seat plate portion 67b, and the valve body shaft 71 is fixedly supported by press-fitting. Yes. Further, adjacent to the rotor shaft hole 72, a communication hole 88 (communication pipe hole 87) to which the communication pipe 69 (69b, 69c, 69d) is connected is opened. FIG. 17 shows one of three communication holes 88 (communication tube holes 87) to which the communication tubes 69 (69b, 69c, 69d) are respectively connected.

  Here, the communication hole 88 and the communication pipe hole 87 are opposite to the side on which the valve body 80 is disposed on the side where the valve body 80 is disposed, and the communication hole 88 having a diameter d0 (for example, about φ1 mm) is opened. The communication tube hole 87 has a diameter d1 enlarged (d1> d0). The communication pipe 69 is fitted and brazed to the portion of the communication pipe hole 87 having the diameter d1.

  The communication hole 88 and the communication pipe hole 87 to which the communication pipe 69 is connected are arranged so as to overlap the communication recess 82 provided in the valve body sliding contact surface 81 by the rotation of the valve body 80.

  On the other hand, the communication pipe 69 generally uses a copper pipe as a refrigerant pipe, and the communication pipe hole 87 into which the communication pipe 69 is fitted and brazed has a diameter d1 (for example, φ3 mm) larger than the inner diameter of the communication hole 88. In order to position the second valve seat plate portion 67b when brazing, a certain depth t2 (for example, about 2 mm) is required.

  Here, the thickness of the second valve seat plate portion 67b is t0, the depth of the bottomed rotor shaft hole 72 is t1, the depth at which the communication pipe 69b, the communication pipe 69c, and the communication pipe 69d are fitted is t2. Then, if the relationship of t0> (t1 + t2) is satisfied, the rotor shaft hole 72 and the communication pipe hole 87 do not interfere with each other so that the hole is not opened. Therefore, it is preferable that the solder does not flow into the rotor shaft hole 72 when the communication pipe 69 is brazed. This can be realized, for example, as t0 = 5 mm and t1 = t2 = 2 mm.

  As shown in FIG. 17, it is preferable that the communication tube hole 87 and the rotor shaft hole 72 do not overlap in the front view of the polished surface 90 because interference between the two is further suppressed.

  Providing the rotor shaft hole 72 in the thick second valve seat plate portion 67b is preferable because the valve body shaft 71 can be press-fitted deeper.

  Next, the suitable structure of the valve seat plate 67 and the valve body axis | shaft 71 is demonstrated using FIG. 17, FIG.

  The valve body shaft 71 is fitted and fixed to the bottomed rotor shaft hole 72 to a depth t1, and is not brazed. Therefore, the valve body shaft 71 and the second valve seat plate portion 67b are not brazed. The wax does not enter the joint, and the surface tension does not protrude into the fillet shape at the corner, and the sticking of the valve body 80 to the second valve seat plate portion 67b is prevented by the protruding wax. There is no effect. Furthermore, when the shaft is fixed by brazing, a clearance of, for example, 0.05 to 0.1 mm is required between the shaft and the shaft hole to allow the wax to flow. In the meantime, a squareness error occurs. That is, even if the rotor shaft hole 72 is drilled at a high perpendicularity with respect to the sliding contact surface of the second valve seat plate portion 67b with the valve body 80, the perpendicularity after brazing of the valve body shaft 71 is achieved. Is inferior to the perpendicularity of drilling.

  On the other hand, in the present embodiment, since the valve body shaft 71 is press-fitted into the rotor shaft hole 72, the valve body shaft 71 is not displaced with respect to the rotor shaft hole 72. Since the accuracy equivalent to the drilling accuracy of 72 is obtained, the valve body shaft 71 is fixed to the valve seat plate 67 without any error, and there is an effect that a high right angle accuracy is obtained.

  Next, preferred dimensions of the communication groove 82 will be described with reference to FIG.

  In (1) the first state and (4) the fourth state of the first embodiment shown in FIG. 15, the refrigerant flows through the communication recess 82.

  Here, as the cross-sectional dimension of the communication recess 82, the width w of the communication recess 82 shown in FIG. 17 is set to a value approximately equal to or slightly larger than the diameter d0 of the communication hole 88, and the depth h of the communication recess 82 shown in FIG. Desirably, the dimensions are approximately equal to w.

  By setting it as such a dimension, when a refrigerant | coolant flows in into the communication recessed part 82 from the communicating port B, C, D, there exists an effect which can suppress the pressure loss by a flow path area expanding rapidly.

  As shown in FIGS. 18 to 19, the inflow pipe 68 or the inflow pipe hole 89 is preferably provided in the first valve seat plate portion 67 a having an intermediate thickness t 4 in the valve seat plate 67. In other words, although a high degree of right-angle accuracy is not required for the positional relationship between the inflow pipe 68 and the inflow pipe hole 89, the first valve seat plate portion 67a has a third outer peripheral surface to ensure strength after brazing. It is desirable that it is not as thin as the valve seat plate portion 67c.

  On the other hand, in order to ensure that the molten wax enters between the inflow pipe 68 and the inflow pipe hole 89, the first valve seat plate portion 67a is the second valve that is the thickest portion where the communication pipe 69 is provided. It is desirable that it is not as thick as the seat plate portion 67b. Furthermore, since the gap between the inflow pipe 68 and the inflow pipe hole 89 is only 0.05 to 0.1 mm, the first valve seat plate portion 67a is formed when the inflow pipe 68 is passed through the inflow pipe hole 89. If the thickness is not excessively thick, the assemblability is better. Therefore, the inflow pipe 68 or the inflow pipe hole 89 is most preferably provided in the first valve seat plate portion 67a having the intermediate thickness t4 in the valve seat plate 67.

  Next, the relationship between the inflow pipe hole 89 formed in the first valve seat plate portion 67a and the inflow pipe 68 will be described with reference to FIG.

  FIG. 20 is a view showing a state before brazing in which the tip of the inflow pipe 68 is widened and temporarily fixed after passing the inflow pipe 68 through the inflow pipe hole 89 formed in the first valve seat plate portion 67a. 20 (a) is a view taken in the direction of arrow J in FIG. 19, FIG. 20 (b) is a sectional view taken along the line KK in FIG. It flows into the valve case 66 through the inflow pipe 68 from below in the figure.

  The inner diameter of the inflow pipe hole 89 is 0.05 to 0.1 mm larger than the outer diameter of the inflow pipe 68, and a gap is formed. This gap is necessary for the molten solder to enter between the inflow pipe 68 and the inflow pipe hole 89 during brazing. If the gap is too small, the wax does not enter, and the inflow pipe 68 becomes inflow pipe hole. 89 is not sealed.

  On the other hand, in the state before brazing, since the inflow pipe 68 and the inflow pipe hole 89 are simply fitted together, the position of the inflow pipe 68 is shifted at the time of brazing if the gap remains. Problems arise. Therefore, it is desirable that the gap necessary for the brazing to flow between the inflow pipe 68 and the inflow pipe hole 89 is maintained and the position does not shift until the brazing is completed by being pressed against each other.

  As an example of such a configuration, as shown in FIG. 20, the inflow pipe 68 protrudes inward from the first valve seat plate portion 67 a by a predetermined convex amount 97, and then the end surface circumference of the inflow pipe 68 is arranged. By partially deforming the end portion of the inflow pipe 68 so as to widen the two places as the widened portion 94 in the upper arrow direction, and press-contacting with the inner side of the inflow pipe hole 89 at the press-contact portion 95 corresponding to the widened portion 94, A gap 96 required for wax to flow between the inflow pipe 68 and the inflow pipe hole 89 can be secured while preventing the displacement between the inflow pipe 68 and the first valve seat plate portion 67a.

  In the present embodiment, the inflow pipe 68 has a configuration in which two places are widened. However, the inflow pipe 68 is not limited to two places, and may be widened in three places, and between the inflow pipe 68 and the inflow pipe hole 89. It suffices if the gap 96 necessary for the wax to flow into can be secured.

  If the two places are widened, the inner end face of the inflow pipe 68 is substantially oval or oval, and if three places are widened, the so-called “diaper shape” is obtained.

  In addition, it is configured so that the wax also wraps around between the inside of the inflow pipe hole 89 and the pressure contact portion 95 due to surface tension.

(Effect of center arrangement of valve body 80)
The valve case 66 and the third valve seat plate portion 67c which is the outer periphery of the valve seat plate 67 shown in FIGS. 9 to 12 are, for example, TIG welding (tungsten / inert gas welding) or It is the structure sealed by laser welding. On the other hand, the valve body 80 and the idler gear 79 (see FIGS. 11 and 13) are made of a heat-resistant resin such as PPS (polyphenylene sulfide resin), but have a limit to the temperature rise. In particular, the valve body sliding contact surface 81 of the valve body 80 may be unable to seal the refrigerant even if slight thermal deformation occurs. Therefore, a configuration that suppresses the temperature rise of the valve body 80 is desirable.

  In the configuration of the refrigerant switching valve 60 according to the first embodiment, the valve body 80 is arranged coaxially with the rotor 70 and around the valve body shaft 71 provided at the center of the valve case 66 and at the center of the valve seat plate 67. It is the structure arrange | positioned so that it may rotate. Therefore, the valve body 80 is disposed at a position farthest from the welded portion 98 as shown in FIG.

  Thereby, since the valve body 80 is disposed at the center position where the heat at the time of welding is hardly transmitted and the temperature is not easily increased, thermal deformation of the valve body 80 at the time of joining the valve case 66 and the valve seat plate 67 can be suppressed. effective.

  Further, as shown in FIGS. 18 to 19, the third valve seat plate portion 67c, which is the outer periphery of the valve seat plate 67, is thinner than the first valve seat plate portion 67a, and the valve seat plate 67 has the smallest thickness. T3. When welding the valve case 66 and the third valve seat plate portion 67c, the temperature of the welded portion needs to rise to a temperature at which the valve case 66 and the third valve seat plate portion 67c melt. The temperature rise of the internal valve body 80 and idler gear 79 must be suppressed. For this purpose, the thickness of the outer peripheral portion that melts at the time of welding can be reduced to sufficiently increase the temperature with a small amount of heat, and the amount of heat conducted to the inner periphery of the valve seat plate 67 can be reduced. desirable.

  For this purpose, the first valve provided between the thickness t3 of the third valve seat plate portion 67c having the thinnest outer periphery and the second valve seat plate portion 67b having the thickest thickness t0 on the inner periphery. By setting the thickness t4 of the seat plate portion 67a to a relationship of t3 <t4 <t0, the third valve seat plate portion 67c as the outer peripheral portion and the outer peripheral portion of the valve case 66 are reliably melted with a small amount of heat. And heat conduction is suppressed by making the thickness of the first valve seat plate portion 67a thinner than that of the second valve seat plate portion 67b, thereby suppressing the temperature rise of the valve body 80 and the idler gear 79. This is preferable because it is possible.

  Next, the details of the surface shape of the valve seat plate 67 that is in sliding contact with the valve body sliding contact surface 81 of the valve body 80 will be described with reference to FIG. 21 is a cross-sectional view showing only the valve seat plate 67 in the FF cross-sectional view shown in FIG.

  The surfaces of the first valve seat plate portion 67a and the second valve seat plate portion 67b facing the valve body 80, that is, the upper surfaces in FIGS. 11, 12, and 17 to 19, are the same plane. The second valve seat plate portion 67b is a sliding surface that opens or closes the communication port B, the communication port C, and the communication port D by the rotation of the valve body 80, and requires high planar accuracy. For this reason, the polished surface 90 is used.

  As shown in FIG. 18 and the like, one surface facing the surface provided with the communication tube hole 87 provided in the second plate portion 67 b is a polished finish surface provided with a communication hole 88 communicating with the communication tube hole 87. 90, and the first plate portion 67a is provided so that one surface thereof is flat and continuous with the polished finish surface 90. The third plate portion 67c is provided so as to be flat and continuous with a surface facing one surface of the first plate portion 67a. The third plate portion 67c may be provided on the side of the surface facing the one surface of the first plate portion 67a.

  The polishing finishing work is performed by, for example, a grinder using a grindstone or a lapping grinder using a slurry-like abrasive, but the outer peripheral edge portion of the polishing finished surface 90 has a pressure contact force with the grindstone rather than the central portion. Since it becomes large and is easily polished, so-called “sag” occurs. That is, on the surface of the valve seat plate 67 on the valve body 80 side, as shown in FIG. 21, a sagging of a depth s occurs in the range e from the outer periphery of the polished finish surface 90. For example, e is about 1-2 mm. , S is about 5 to 10 μm.

  In the inner range excluding the range e from the outer periphery, no sagging occurs, so that a surface with high surface accuracy is obtained. Here, if the diameter of the valve body sliding contact surface 81 is d, the range of the diameter d is provided in the inner periphery sufficiently from the outer periphery to the range e, so that there is no influence of sagging due to polishing, and the valve body sliding contact is achieved. Since the surface 81 and the valve seat plate 67 can be slid in contact with each other with high accuracy, there is an effect that the sealing performance is improved, the refrigerant leakage is reduced, and the switching accuracy of the valve can be improved.

Next, preferred shapes of the first valve seat plate portion 67a, the third valve seat plate portion (outer peripheral valve seat plate portion) 67c, and the valve case 66 will be described with reference to FIG.
FIG. 22 is a cross-sectional view showing the vicinity of the welded portion 98 on the outer periphery of the valve seat plate 67 and the valve case 66.

  A first valve seat plate portion 67a having a thickness t4 and a diameter D1, and a third valve seat plate portion (outer peripheral valve seat plate portion) 67c having a thickness t3 of the outer peripheral portion, If the illustrated lower surface of the third valve seat plate portion 67c is arranged to be the same surface, a step is formed between the illustrated upper surface of the first valve seat plate portion 67a and the illustrated upper surface of the third valve seat plate portion 67c. H is generated. Here, H = (t4-t3).

  The lower end of the valve case 66 opened with a diameter D1 forms an enlarged portion that is larger than D1 in a flange shape or a bowl shape, and the outer peripheral diameter thereof is the same as or substantially the same as the outer periphery of the third valve seat plate portion 67c. equal. A welded portion 98 of the entire circumference at the boundary between the outer periphery of the valve case 66 and the outer periphery of the third valve seat plate portion 67c is sealed and joined by welding.

  When welding, the valve case 66 and the valve seat plate 67 must be coaxially welded with high accuracy. Since the valve case 66 is integrally formed by deep drawing or the like, the inner peripheral ridge line portion of the enlarged portion expanded from the cylindrical shape of the diameter D1 to the flange shape is equal to the plate thickness of the valve case 66 or the plate. The cross-sectional shape has a bending radius slightly larger than the thickness.

  Therefore, the step H between the illustrated upper surface of the first valve seat plate portion 67a and the illustrated upper surface of the third valve seat plate portion 67c is larger than the bending R of the valve case 66, that is, H> R. In other words, the enlarged portion formed by the bending R is located within the height dimension of the step H. Thereby, in the range (HR) from the upper surface of the first valve seat plate portion 67a in the drawing, that is, in the upper position of the enlarged portion, the inner periphery of the valve case 66 and the outer periphery of the first valve seat plate portion 67a. Are fitted to each other in the cylindrical portion of the diameter D1, and the inner periphery of the valve case 66 and the outer periphery of the first valve seat plate portion 67a can be accurately positioned coaxially, and high coaxiality can be secured even after welding. It is.

<Action and effect>
1. The refrigerant switching valve 60 improves the refrigerant switching performance by switching the valve body 80.

  As shown in FIGS. 14-16, the refrigerant | coolant switching valve 60 which concerns on 1st Embodiment switches the valve body 80, and the inflow pipe 68 (inflow port A) shown in FIG. The communication port B), the communication tube 69c (communication port C), and the communication tube 69d (communication port D) do not communicate with each other, and the communication tube 69b (communication port B) and the communication tube 69c (communication port C) are connected. The first state (refrigerant recovery mode) in which the communication pipe 69d (communication port D) is closed with each other, and the inflow pipe 68 (inflow port A) and the communication pipe 69d (communication port D) shown in FIG. In addition, the second state (stop mode) in which the communication pipe 69b (communication port B) and the communication pipe 69c (communication port C) are closed, and the communication with the inflow pipe 68 (inlet A) shown in FIG. The tube 69c (communication port C) communicates with the communication tube 69b (communication port B). The third state (bypass mode) in which the pipe 69d (communication port D) is closed, and the inflow pipe 68 (inflow port A) and the communication pipe 69b (communication port B) shown in FIG. The fourth state (condensation prevention mode) in which the tube 69c (communication port C) and the communication tube 69d (communication port D) communicate with each other can be switched.

  Thereby, the refrigerant switching valve 60 with improved refrigerant switching performance can be provided. In addition, the refrigerant can be switched in accordance with the actual use state of the device (refrigerator 1) provided with the refrigerant switching valve 60.

  2. The mode of the refrigerator 1 of the device can be switched by the refrigerant switching valve 60.

  As described with reference to FIGS. 5 to 8 and FIGS. 14 to 16, the device (refrigerator 1) provided with the refrigerant switching valve 60 according to the first embodiment supplies a refrigerant having a temperature higher than the outside air to the condensation prevention pipe 17. A first mode for preventing condensation (see FIGS. 5 and 16 (4)), a second mode for reducing heat leakage from the condensation prevention pipe 17 (see FIGS. 6 and 16 (3)), and a compressor. A third mode (see FIGS. 7 and 16 (2)) that maintains the temperature of the refrigerant in the cooler 7 at a low temperature when stopping 51, and a fourth mode (see FIG. 7 and FIG. 16 (2)) that reduces the amount of refrigerant in the dew condensation prevention pipe 17. The modes of the four refrigerant paths (refrigerant circuits) with reference to FIGS. 8 and 16 (1)) can be switched by the operation of the single refrigerant switching valve 60.

  Thereby, the valve provided in the refrigerant | coolant path | route (refrigerant circuit) of an apparatus (refrigerator 1) is only the refrigerant | coolant switching valve 60, and since it can comprise a refrigerating cycle without adding another valve, it can comprise at low cost. Moreover, since the switching control and arrangement of the refrigerant switching valve 60 are not complicated, the reliability of the device (refrigerator 1) including the refrigerant switching valve 60 can be improved.

  Alternatively, the fourth mode for reducing the amount of refrigerant in the condensation prevention pipe 17 is not provided, and the first mode (see FIGS. 5 and 16 (4)) for preventing condensation and heat leakage from the condensation prevention pipe 17 are reduced. A second mode (see FIGS. 6 and 16 (3)), and a third mode (FIGS. 7 and 16 (2)) that maintains the temperature of the refrigerant in the cooler 7 at a low temperature when the compressor 51 is stopped. Reference) may be provided.

  3. Switching between the condensation prevention mode and the bypass mode (a mode in which the refrigerant does not flow through the condensation prevention pipe 17) can be performed.

  The apparatus (refrigerator 1) provided with the refrigerant switching valve 60 can be used when the outside air is hot and humid and there is a risk of condensation depending on the measurement results of the outside air humidity sensor 43 and the outside air temperature sensor 42 shown in FIG. When the (refrigerant circuit) is switched to the first mode (condensation prevention mode) (see FIGS. 5 and 16 (4)) and the outside air is low in humidity and there is no risk of condensation, the refrigerant path (refrigerant circuit) is switched to the second mode. It is possible to switch to a mode (bypass mode) (see FIGS. 6 and 16 (3)). This mode can be switched by the operation of the refrigerant switching valve 60 as described above.

  Thereby, when there is a possibility of condensation, a high-temperature refrigerant is passed through the condensation prevention pipe 17, and the temperature of the opening front peripheral edge 1H2 of the storage chamber (3, 4, 5) is set higher than the storage chamber temperature. Dew point can be raised to prevent condensation. Moreover, when there is no possibility of dew condensation, it is possible to stop the passage of the refrigerant through the dew condensation prevention pipe 17 and to prevent the heat from the dew condensation prevention pipe 17 from leaking into the storage chamber and increasing the energy consumption. Therefore, there is an energy saving effect and the operating cost can be reduced.

  4). It is possible to speed up the mode switching.

  In the first mode (condensation prevention mode) (see FIGS. 5 and 16 (4)) and the second mode (bypass mode) (see FIGS. 6 and 16 (3)), the rotation angle of the valve body 80 is set to 90. It can be switched by rotating °. Therefore, switching between the first mode that passes through the condensation prevention pipe 17 and the second mode that does not pass through the condensation prevention pipe 17 can be performed in a very short time.

  5. It has the effect of preventing choke operation.

  Here, a first mode (condensation prevention mode) that passes through the dew condensation prevention pipe 17 (see FIGS. 5 and 16 (4)) and a second mode (bypass mode) that does not pass through the dew condensation prevention pipe 17 (FIGS. 6 and 6). 16 (3)) is switched to the third mode (stop mode) in which the compressor 51 is stopped (see FIGS. 7 and 16 (2)) or the fourth is to reduce the amount of refrigerant in the dew condensation prevention pipe 17. The problem of the configuration in which the mode (refrigerant recovery mode) (see FIGS. 8 and 16 (1)) is switched once is described.

  In both the third mode (stop mode) and the fourth mode (refrigerant recovery mode), the inlet A communicated with the high-pressure side discharge port 51o of the compressor 51 and the communication port communicated with the low-pressure side suction port 51i of the compressor 51. C does not communicate, and the refrigerant circuit is closed. Therefore, when the compressor 51 is operated in this state, the pressure at the high-pressure side discharge port 51o increases and the pressure at the low-pressure side suction port 51i decreases, but the refrigerant does not flow, so that the compressor 51 only idles. It becomes a state. It is not preferable to operate the compressor 51 in such a state because an excessive pressure rise occurs.

  Accordingly, the first mode (condensation prevention mode) (see FIGS. 5 and 16 (4)) that passes through the condensation prevention pipe 17 and the second mode (bypass mode) that bypasses the condensation prevention pipe 17 (FIGS. 6 and 16). When switching between (see (3)), the third mode (stop mode) (see FIGS. 7 and 16 (2)) to the fourth mode (refrigerant recovery mode) (see FIGS. 8 and 16 (1)). In the case of a configuration that goes through once, it is desirable to stop the compressor 51 each time, but every time the first mode (condensation prevention mode) and the second mode (bypass mode) are switched, the compressor 51 is stopped and restarted. There is a problem that it takes a long time to switch the mode because a step of starting is required.

  On the other hand, when the first mode and the second mode are switched while the compressor 51 is operated, the third mode (stop mode) to the fourth mode (refrigerant recovery mode) while the compressor 51 is operated during the switching operation. ), The operation is in a choked state, which is not preferable for the compressor 51.

  According to the first embodiment, when switching between the first mode (condensation prevention mode) that passes through the condensation prevention pipe 17 and the second mode (bypass mode) that does not pass through the condensation prevention pipe 17, no other mode is passed. Therefore, even if the switching operation is performed while the compressor 51 is operated, the operation is not performed in a choked state, the switching operation can be performed in a short time, and an excessive pressure increase of the compressor 51 does not occur. The reliability of the device (refrigerator 1) provided with the switching valve 60 can be improved.

  In the first embodiment, as illustrated in FIGS. 14 to 16, the communication port B, the communication port C, and the communication port D are sequentially arranged at 90 ° in the illustrated clockwise direction. 15 and 16, if the shape of the valve body sliding contact surface 81 and the rotational operation direction are mirror images that are symmetrical to those shown in the figure, even if they are arranged every 90 ° in the counterclockwise direction opposite to those shown in FIG. Switching between the communication ports B, C, and D and the switching operation of the refrigerant circuit similar to those shown are possible.

  6). Piping can be simplified.

  Conventionally, a configuration in which a refrigerant switching valve and a refrigerant backflow prevention valve are provided to switch between a dew condensation prevention mode (first mode) that passes through the dew condensation prevention pipe 17 and a bypass mode (second mode) that bypasses the dew condensation prevention pipe 17. In this case, the refrigerant switching valve, which is a four-way valve, has one inflow pipe and three communication pipes, and the refrigerant backflow prevention valve has one inflow pipe and one outlet pipe, and therefore is connected to the refrigerant circuit. To do this, it is necessary to connect at least six places by brazing.

  In contrast, in the refrigerant switching valve 60 according to the first embodiment (the present invention), the refrigerant switching valve 60 includes one inflow pipe 68 and three communication pipes as shown in FIGS. 69 (69a, 69b, 69c) are provided for a total of four pipes, and no other refrigerant backflow prevention valve is required, so four points are brazed to connect the refrigerant switching valve 60 to the refrigerant circuit. It is sufficient to reduce the number of brazing points and reduce the cost.

  Further, in the case of a configuration including a conventional refrigerant switching valve and a refrigerant backflow prevention valve, there is no refrigerant backflow prevention valve for connecting a part of the refrigerant pipe to one end and the other end of the refrigerant backflow prevention valve. The length of the refrigerant pipe is longer than In the first embodiment (the present invention), since the refrigerant backflow prevention valve is not provided, there is no need to increase the length of the refrigerant pipe, and the material of the refrigerant pipe is saved, which is effective for resource protection.

  In the above description, the configuration including the conventional refrigerant switching valve and the refrigerant backflow prevention valve has been described in comparison with the first embodiment. However, for comparison with the configuration provided with the refrigerant backflow prevention valve. The present embodiment is not limited, and the first embodiment can reduce the brazed portion and increase the length of the refrigerant pipe even when compared with a configuration including two sets of refrigerant switching valves that are conventional solenoid valves. It is clear that the material for the refrigerant pipe is saved and the resource protection is effective.

  7). Adhesion is improved by the pressure of the refrigerant.

  In the refrigerant switching valve 60 of the first embodiment, the high-pressure refrigerant from the compressor 51 passes through the first refrigerant pipe 55 (see FIG. 5), the inflow pipe 68 (see FIG. 11), and the inlet A (see FIG. 10). And flows into the space inside the valve case 66.

  Therefore, the pressure of the refrigerant is applied to the valve body 80 in the valve case 66 shown in FIG. 11 as a force in a direction in which the valve body 80 is pressed against the valve seat plate 67. Thereby, the adhesiveness between the valve body sliding contact surface 81 of the valve body 80 and the valve seat plate 67 improves, and the leakage of a refrigerant | coolant can be reduced.

  8). The refrigerant switching valve 60 (projected area thereof) can be downsized.

  As shown in FIG. 11, in the refrigerant switching valve 60 of the first embodiment, a rotor pinion gear 75 that rotates integrally with the rotor 70 and the rotor drive unit 74 is overlapped on the valve body 80, and the rotor pinion gear 75 and the valve body 80 are overlapped. Are arranged so as to be rotatable around a valve body shaft 71 which is a common rotation shaft. Further, an idler gear 79 in which an idler large gear 79b and an idler pinion gear 79a are integrally provided is arranged around an idler shaft 78 provided separately from the valve body shaft 71.

  Then, the rotor pinion gear 75 and the idler large gear 79b mesh with each other to decelerate, and the idler pinion gear 79a and the valve body gear 83 mesh with each other to further decelerate. Accordingly, the three gears of the rotor pinion gear 75, the idler gear 79, and the valve body gear 83 can be disposed around the two shafts of the valve body shaft 71 and the idler shaft 78.

  Therefore, three gears can be arranged in the projected area of the two gears, and the refrigerant switching valve 60 can be downsized.

  9. The rotational torque of the valve body 80 can be increased.

  Since the two-stage deceleration is performed from the rotor pinion gear 75 to the valve body gear 83, the reduction ratio is increased, and the rotational torque transmitted to the valve body 80 can be increased. Therefore, the switching operation of the valve body 80 can be performed reliably.

  Further, even if the friction between the valve body 80 and the valve seat (second valve seat plate portion 67b) increases, the rotational torque does not become insufficient (the rotational torque is large). It is not necessary to use a special low friction material. Moreover, even if a combination of a stator and a rotor having a low rotational torque can be operated with an increased rotational torque, the refrigerant switching valve 60 can be reduced in price.

  10. An appropriate pressing force to the second valve seat plate portion 67b of the valve body 80 can be secured.

  As shown in FIG. 11, in the refrigerant switching valve 60, the rotor 70 (rotor driving unit 74, rotor pinion gear 75) and the valve body 80 are coaxially arranged with a common valve body shaft 71, and the rotor 70 (rotor driving unit 74, The rotor pinion gear 75) is placed on the valve body 80, and the rotor 70 (the rotor drive unit 74, the rotor pinion gear 75) is urged by the leaf spring 86.

  Thereby, the valve body 80 is urged | biased with respect to a valve seat (2nd valve seat plate part 67b) by the urging | biasing force of the leaf | plate spring 86, and the dead weight of the rotor 70 (rotor drive part 74, rotor pinion gear 75). Therefore, the valve body sliding contact surface 81 is pressed against the valve seat (second valve seat plate portion 67b) with an appropriate pressing force, and a pressing force for reliably closing the refrigerant can be obtained.

  11. The valve body shaft 71 can have a simple both-end support structure.

  As shown in FIG. 11, in the refrigerant switching valve 60, the valve body shaft 71 that supports the valve body 80 is provided on the second valve seat plate portion 67 b of the valve seat that contacts the valve body 80 at the valve body sliding contact surface 81. This is a double-supported structure in which both ends are supported by a rotor bearing 73 which is a recessed portion provided at the upper end of the valve case 66 and is press-fitted and supported in the bottomed rotor shaft hole 72.

  Therefore, the support rigidity and accuracy of the valve body 80 can be easily obtained, and the refrigerant can be reliably closed at the valve body sliding contact surface 81. In addition, since the rotor 70 (the rotor drive unit 74 and the rotor pinion gear 75) rotates around the valve body shaft 71, it is not necessary to provide a highly accurate bearing in the rotor shaft hole 72 and the rotor bearing 73, and the refrigerant The price of the switching valve 60 can be reduced.

  Further, since the rotor 70 and the valve body 80 that require rotational accuracy are provided around the valve body shaft 71, and the rotor 70 and the valve body 80 rotate about the same axis, it is easy to obtain a coaxial degree and rotational accuracy. Is expensive.

  12 Since the idler shaft 78 has a cantilever structure, the assembly of the refrigerant switching valve 60 is improved.

  As shown in FIG. 11, in the refrigerant switching valve 60 according to the first embodiment, the idler shaft 78 has a cantilever structure, and the assemblability of the refrigerant switching valve 60 is improved. Even when the idler gear 79 moves in the upward direction, the idler large gear 79b contacts the rotor drive unit 74, so that the idler gear 79 can be prevented from falling off.

  As described above, it is desirable to reduce the contact area between the rotor drive unit 74 and the idler large gear 79b by forming the projection 74s on the rotor drive unit 74 and forming the projection 79s on the idler gear 79. . As a result, an increase in extra frictional force can be avoided.

  13. The valve seat plate 67 is integrated, and the communication pipe 69 is provided in the thickest part.

  The problem when the first valve seat plate portion 67a and the second valve seat plate portion 67b are joined to each other by brazing will be described. The solder from the joint portion becomes the second valve seat plate portion 67b. In such a case, there is a problem that the valve body sliding contact surface 81 cannot hermetically seal the communication ports B, C, and D.

  On the other hand, in the present embodiment, since the first valve seat plate portion 67a and the second valve seat plate portion 67b are integrated, the leaching of wax to the surface of the valve seat plate 67 is prevented and the refrigerant is reliably sealed. There is an effect that can be stopped.

  Furthermore, if the diameter of the valve body sliding contact surface 81 is d, the range of the diameter d is provided in the inner periphery sufficiently more than the range in which polishing sagging occurs from the outer periphery, so that there is no influence of sagging due to polishing. Since the body-sliding contact surface 81 and the valve seat plate 67 can be slidably contacted with high accuracy without a gap, there is an effect that the sealing performance is improved, the refrigerant leakage is reduced, and the valve switching accuracy is improved.

Further, as shown in FIGS. 11 to 17, in the refrigerant switching valve 60 according to the first embodiment, the valve seat plate 67 has a communication pipe 69 connected to the second valve seat plate portion 67b having the maximum thickness at the center. Provided. By providing the communication tube hole 87 in the thickest part of the valve seat plate 67, the insertion depth of the communication tube 69 into the communication tube hole 87 can be secured.
14 The accuracy of the rotor shaft is improved by press-fitting the rotor shaft into the bottomed rotor shaft hole 72.

  The rotor shaft hole 72 provided in the center of the second valve seat plate portion 67b is a bottomed hole, and the valve body shaft 71 is press-fitted and fixed without a gap.

If the thickness of the second valve seat plate portion 67b is t0, the depth of the bottomed rotor shaft hole 72 is t1, and the depth at which the communication pipe 69b, the communication pipe 69c, and the communication pipe 69d are fitted is t2. If the relationship of t0> (t1 + t2) is satisfied, the rotor shaft hole 72 and the communication tube hole 87 do not interfere with each other and the hole is not opened. Therefore, it is preferable that the solder does not flow into the rotor shaft hole 72 when the communication pipe 69 is brazed. Further, since the valve body shaft 71 is press-fitted and fixed to the rotor shaft hole 72 without a gap, the valve body shaft 71 can easily secure a squareness with respect to the second valve seat plate portion 67b, and high accuracy can be obtained.
15. The valve seat plate 67 is configured to be concentric with the thinnest outer peripheral portion, the thickest central portion provided with the communication pipe, and the intermediate thickness between the outer peripheral portion and the central portion. Deformation can be prevented.

A communication pipe for inserting and brazing the communication pipe 69 by reducing the amount of heat required for welding by making the outer peripheral part (third valve seat plate part 67c) heated for welding with the valve case 66 the thinnest. By thickening the central portion (second valve seat plate portion 67b) provided with the hole 87, the communication pipe 69 is fixed securely and the valve body shaft 71 is press-fitted and supported in the bottomed rotor shaft hole 72. Since the thickness between the outer peripheral portion and the central portion (the first valve seat plate portion 67a) is an intermediate thickness, heat at the time of welding is hardly transmitted to the valve body 80 in the central portion, and the heat of the valve body 80 Since the deformation can be prevented, the contact with the valve seat plate 67 is improved by maintaining the valve body sliding contact surface 81 of the valve body 80 with high accuracy, and the leakage of the refrigerant can be reduced.
16. Since the inflow pipe is provided at the intermediate thickness portion, the assemblability is good.

Since the inflow pipe hole 89 is provided in the first valve seat plate portion 67a having the intermediate thickness t4 in the valve seat plate 67, the wax surely enters the gap between the inflow pipe 68 and the inflow pipe hole 89. Thus, it is possible to securely seal and sufficiently secure the strength after brazing.
Furthermore, the workability when penetrating the inflow pipe 68 through the inflow pipe hole 89 is good.
17. The inflow pipe was partially widened and temporarily fixed.

  After the inflow pipe 68 is arranged to protrude from the first valve seat plate portion 67a by a predetermined convex amount 97, the end of the inflow pipe 68 is partially deformed so as to widen two or three places on the end surface circumference. The inflow pipe hole 89 is in pressure contact with the inflow pipe hole 89 at the press-contact portion 95, so that the inflow pipe 68 and the first valve seat plate portion 67a are pressed against each other to prevent positional displacement, and the inflow pipe 68 and the inflow pipe hole 89 There is an effect that a gap necessary for the flow of wax can be secured between them.

  Furthermore, since the inflow pipe 68 is disposed so as to protrude from the first valve seat plate portion 67 a by a predetermined convex amount 97, the wax that has oozed out on the surface of the first valve seat plate will enter the inside of the inflow pipe 68. There is also an effect of preventing intrusion.

  Furthermore, since the inflow pipe 68 is disposed so as to protrude from the first valve seat plate portion 67a by a predetermined convex amount 97, the fluid discharged from the inflow pipe 68 flows upward, so that the valve body 80 is caused by the fluid. There is also an effect that can be pressed downward from above. In this case, the predetermined convex amount 97 is preferably higher than the valve body sliding contact surface 81.

  18. The welding accuracy with the valve case can be improved by the level difference of the valve seat plate.

  If the step H on the valve case 66 side generated between the first valve seat plate portion 67a and the third valve seat plate portion 67c is larger than the bending R of the valve case 66, that is, H> R, the valve body 80 In the range of (HR) from the sliding contact surface, the inner periphery of the valve case 66 and the outer periphery of the first valve seat plate portion 67a are fitted to each other by the cylindrical portion having the diameter D1, The inner circumference and the outer circumference of the first valve seat plate portion 67a can be positioned coaxially with high accuracy, and high coaxiality can be secured even after welding.

  Next, the refrigerant switching valve according to the second embodiment will be described with reference to FIG. In FIG. 23, the valve body sliding contact surface 81A in contact with the valve seat plate 67 is shown with hatching for explanation. FIG. 23 (A) is an explanatory view showing the internal configuration of the first state of the refrigerant switching valve according to the second embodiment, and FIG. 23 (B) is the inside of the second state of the refrigerant switching valve according to the second embodiment. It is explanatory drawing which shows a structure, FIG.23 (C) is explanatory drawing which shows the internal structure of the 3rd state of the refrigerant | coolant switching valve which concerns on 2nd Embodiment.

  The refrigerant switching valve according to the first embodiment is a four-way valve, whereas the refrigerant switching valve according to the second embodiment is a three-way valve, and an inlet A, a communication port B, and a communication port D are provided in the valve seat plate 67. It is different in that the communication port C is not formed.

  Further, in the valve body 80 of the first embodiment, the communication recess 82 is formed in the valve body sliding contact surface 81, whereas in the valve body 80A of the third embodiment, the communication recess is connected to the valve body sliding contact surface 81A. Is different in that is not formed.

  FIG. 23A shows a first state in which the communication port B opens into the valve case 66 and the communication port D is covered with the valve body 80A. In this first state, the inflow port A communicates with the communication port B, and the communication port D is closed.

  FIG. 23B shows a second state in which the communication port B and the communication port D are covered with the valve body 80A, and the valve body 80A is rotated 90 ° counterclockwise from the first state (see FIG. 23A). It is in a state of swinging. In the second state, the communication port B and the communication port D are closed, and neither is the communication with the inflow port A.

  FIG. 23 (C) shows a third state in which the communication port B is covered with the valve body 80A and the communication port D is opened inside the valve case 66, and the valve body from the second state (see FIG. 23 (B)). In this state, 80A is swung 90 ° counterclockwise. In the third state, the inflow port A communicates with the communication port D, and the communication port B is in a closed state.

  When the state communicating with the inlet A is “open”, the state not communicating with the inlet A is “closed”, and the states of the communication port B and the communication port D are expressed in the form of “communication port B / communication port D”. The refrigerant switching valve according to the second embodiment can take three states of “open / closed”, “closed / closed”, and “closed / opened”. That is, when only the communication port B is switched from the open state (see FIG. 23A) to the communication port D only in the open state (see FIG. 23C), the communication port B and the communication port D are closed (see FIG. 23). 23 (B)).

  The refrigerant switching valve according to the second embodiment can function as a three-way valve with the same configuration as the refrigerant switching valve according to the first embodiment. In addition, the refrigerant can be switched between flow and shut-off quickly, the adhesion performance between the valve body sliding contact surface 81A and the valve seat plate 67 is improved, and the reliability of suppressing the leakage of the refrigerant is improved. be able to.

«Third embodiment»
Next, the refrigerant switching valve according to the third embodiment will be described with reference to FIGS. 24 and 25. In FIG. 25, the valve body sliding contact surface 81B in contact with the valve seat plate 67 is shown with hatching for explanation. FIG. 24 is a perspective view of a valve body 80B provided in the refrigerant switching valve according to the third embodiment. FIG. 25 (A) is an explanatory view showing the internal configuration of the first state of the refrigerant switching valve according to the third embodiment, and FIG. 25 (B) is the inside of the second state of the refrigerant switching valve according to the third embodiment. It is explanatory drawing which shows a structure, FIG.25 (C) is explanatory drawing which shows the internal structure of the 3rd state of the refrigerant | coolant switching valve which concerns on 3rd Embodiment. FIG. 25D is an explanatory diagram showing the internal configuration of the fourth state of the refrigerant switching valve according to the third embodiment.

  The refrigerant switching valve according to the first embodiment is a four-way valve, whereas the refrigerant switching valve according to the third embodiment is a three-way valve, and an inlet A, a communication port C, and a communication port D are provided in the valve seat plate 67. It is different in that it is formed and the communication port B is not formed.

  In the valve body 80 of the first embodiment, the area of the valve body sliding contact surface 81 is large enough to block the three communication ports (see FIG. 15 (1)), and the communication recess 82 is formed. On the other hand, the valve body 80B of the third embodiment has a size capable of closing two communication ports (communication port C and communication port D) where the area of the valve body sliding contact surface 81B is adjacent (FIG. 25). (See (A)), and the communication recess is not formed. Further, the difference is that the shape of the stopper 84B of the valve body 80B and the arrangement angle of the valve body gear 83 are expanded so as to increase the swing angle of the valve body 80B.

  FIG. 25A shows a first state in which the communication port C and the communication port D are covered with the valve body 80B. In this first state, the communication port C and the communication port D are closed and are not in communication with the inflow port A.

  FIG. 25B shows a second state in which the communication port C is opened in the valve case 66 and the communication port D is covered with the valve body 80B, and the valve is changed from the first state (see FIG. 25A). In this state, the body 80B is swung 90 ° counterclockwise. In this second state, the inflow port A communicates with the communication port C, and the communication port D is closed.

  FIG. 25C shows a third state in which the communication port C and the communication port D are opened inside the valve case 66, and the valve body 80B is rotated 90 ° counterclockwise from the second state (see FIG. 25B). It is in a state of swinging. In this third state, the inflow port A is in a state of communicating with the communication port C and the communication port D.

  FIG. 25 (D) shows a fourth state in which the communication port C is covered with the valve body 80 and the communication port D is opened inside the valve case 66, and the valve body from the third state (see FIG. 25 (C)). In this state, 80B is swung 90 ° counterclockwise. In the fourth state, the inflow port A communicates with the communication port D, and the communication port C is closed.

  When the state communicating with the inlet A is “open”, the state not communicating with the inlet A is “closed”, and the states of the communication port C and the communication port D are expressed in the form of “communication port C / communication port D”. The refrigerant switching valve according to the third embodiment can take four states of “closed / closed”, “open / closed”, “open / opened”, and “closed / opened”.

  In addition, the refrigerant switching valve according to the third embodiment is operated between the second state and the fourth state, so that three states of “open / closed”, “open / open”, and “closed / open” are set. Can take. That is, when only the communication port C is switched from the open state (see FIG. 25B) to only the communication port D is switched to the open state (see FIG. 25D), the communication port C and the communication port D are in the open state (see FIG. 25). 25 (C)).

  The refrigerant switching valve according to the third embodiment can function as a three-way valve with the same configuration as the refrigerant switching valve according to the first embodiment. In addition, it is possible to quickly switch between the circulation and the blocking of the refrigerant, and the adhesion performance between the valve body sliding contact surface 81B and the valve seat plate 67 is improved, thereby improving the reliability of suppressing the leakage of the refrigerant. be able to.

<< Fourth Embodiment >>
Next, the refrigerant switching valve according to the fourth embodiment will be described with reference to FIG. In FIG. 26, the valve body sliding contact surface 81A in contact with the valve seat plate 67 is illustrated with hatching for the sake of explanation.

  FIG. 26A is an explanatory view showing the internal configuration of the first state of the refrigerant switching valve according to the fourth embodiment, and FIG. 26B is the inside of the second state of the refrigerant switching valve according to the fourth embodiment. It is explanatory drawing which shows a structure.

  The refrigerant switching valve according to the first embodiment is a four-way valve, whereas the refrigerant switching valve according to the fourth embodiment is a two-way valve, and an inlet A and a communication port D are formed in the valve seat plate 67, The difference is that the communication port B and the communication port C are not formed.

  Further, the valve body 80A of the fourth embodiment is the same as the valve body 80A of the second embodiment, and is different in that no communicating recess is formed on the valve body sliding contact surface 81A.

  FIG. 26A shows a first state where the communication port D is covered with the valve body 80A. In this first state, the communication port D is in a closed state and is not in communication with the inflow port A.

  FIG. 26B shows a second state in which the communication port D is opened inside the valve case 66, and the valve body 80A is swung 180 ° counterclockwise from the first state (see FIG. 26A). State. In this second state, the inflow port A is in a state of communicating with the communication port D.

  When the state communicating with the inlet A is “open”, the state not communicating with the inlet A is “closed”, and the state of the communication port D is expressed in the form of “communication port D”, refrigerant switching according to the fourth embodiment The valve can take two states, “open” and “closed”.

  The refrigerant switching valve according to the fourth embodiment can function as a two-way valve with the same configuration as the refrigerant switching valve according to the first embodiment. In addition, the refrigerant can be switched between flow and shut-off quickly, the adhesion performance between the valve body sliding contact surface 81A and the valve seat plate 67 is improved, and the reliability of suppressing the leakage of the refrigerant is improved. be able to.

≪Operation during liquid sealing≫
Next, a case where a so-called liquid seal occurs in the refrigerant path (refrigerant circuit) will be described with reference to FIG. Here, the liquid seal is a refrigerant circuit whose both ends are closed, that is, the closed circuit is filled with a liquid refrigerant, and then the temperature rises and the refrigerant thermally expands, so that the refrigerant expands inside the piping of the refrigerant circuit or inside the valve body. This is a phenomenon in which high pressure occurs.

  As described above, for example, in the third state (see FIG. 16 (3)) of the refrigerant switching valve 60 according to the first embodiment, the second refrigerant pipe 56 (and the dew condensation prevention pipe 17) are valve bodies 80 at both ends. The closed circuit is closed.

(Liquid ring prevention in the third state of the first embodiment)
Incidentally, for example, in the third state (see FIG. 16 (3)) of the refrigerant switching valve 60 according to the first embodiment, the valve case 66 is in a state of communicating with the condenser 52 having a relatively large volume. Since the volume of the closed circuit (condenser 52, first refrigerant pipe 55, valve case 66) can be made larger than the volume of the total amount of refrigerant enclosed (when liquid), liquid sealing can be prevented. .

  Further, the third refrigerant pipe 57 and the cooler 7 that are closed by the communication port C of the refrigerant switching valve 60 and the compressor 51 also have a relatively large volume inside the cooler 7 that functions as an evaporator. Sealing can be prevented.

  FIG. 27 is an enlarged partial cross-sectional view showing a cross section of the second valve seat plate portion 67b, the valve body 80, and the communication pipe 69 of the refrigerant switching valve 60 when the pressure on the communication pipe 69 side increases.

  When all of the inside of the closed circuit is filled with liquid refrigerant and then the temperature rises and the refrigerant thermally expands, the pressure P2 of the thermally expanded refrigerant is directed from the communication pipe 69 to the valve body 80 (from the lower side to the upper side in the drawing). Join.

  By the way, as described with reference to FIGS. 11 to 12, the valve body 80 is configured such that the rotor 70 (the rotor driving unit 74 and the rotor pinion gear 75) is placed on the rotor 70 (the rotor driving unit 74 and the rotor pinion gear 75). ) And the urging force of the leaf spring 86 are preloaded against the second valve seat plate portion 67b. Further, a pressing force resulting from the refrigerant pressure P <b> 1 inside the valve case 66 is applied to the valve body 80.

  Here, the pressure P2 of the refrigerant becomes larger than P1, and receives a force exceeding the total weight of the rotor 70 (rotor driving unit 74, rotor pinion gear 75), the urging force of the leaf spring 86, and the pressing force caused by the pressure P1. 27, the leaf spring 86 contracts, and the valve body 80 and the rotor 70 (the rotor drive unit 74 and the rotor pinion gear 75) are moved from the second valve seat plate portion 67b along the valve body shaft 71 as shown in FIG. Move in the direction of ascent. As the valve body 80 rises, the refrigerant in the communication pipe 69 flows into the valve case 66 from the gap between the valve body 80 and the second valve seat plate portion 67b, and the pressure in the communication pipe 69 is increased. descend. When the pressure in the communication pipe 69 decreases, the valve body 80 comes into close contact with the second valve seat plate portion 67b by the own weight of the rotor 70 (rotor drive portion 74, rotor pinion gear 75) and the urging force of the leaf spring 86. To do.

  Thus, since the valve body 80 can float from the 2nd valve seat plate part 67b, there exists an effect that it can suppress that the pressure in the communicating pipe 69 raises abnormally.

  The effect of suppressing the abnormal increase in the pressure in the communication pipe 69 is not limited to the liquid-sealed state in which the inside of the communication pipe 69 is filled with the liquid refrigerant. The same effect can be obtained when the pressure is increased due to thermal expansion due to temperature rise.

  In the first embodiment, the communication ports B, C, and D are arranged at the apex position of the square. However, the opening / closing operation of the communication port according to the rotation of the valve body 80 of the first embodiment is the same. If so, the angle of the adjacent communication port may be shifted from 90 °.

«Fifth embodiment»
Next, the refrigerant switching valve according to the fifth embodiment will be described with reference to FIG.

  FIG. 28 is a cross-sectional view similar to FIG. 18 showing the configuration of the refrigerant switching valve 60 according to the fifth embodiment. The difference from FIG. 18 is that the diameter of the second valve seat plate portion 67b is enlarged and substantially the first The inflow pipe 68 is provided not in the first valve seat plate section 67a but in the second valve seat plate section 67b, close to the diameter of the valve seat plate section 67a, and the inflow pipe 68 is provided in the second valve seat plate section 67b. In the side where the valve body 80 is arranged without penetrating into the valve, the inlet A having a diameter of, for example, about φ2 mm is opened, and the diameter of the inlet pipe hole 89 on the opposite side to the side where the valve body 80 is arranged is enlarged. Has been. The inflow pipe 68 is fitted and brazed to a portion where the diameter of the inflow pipe hole 89 is enlarged.

<< Other Embodiments >>
1. In the first to fifth embodiments, a case where the valve body 80 and the rotor 70 are coaxial in the refrigerant switching valve 60, a case where a speed reduction mechanism is provided between the rotor drive unit 74 and the valve body 80, and the like are exemplified. As described above, if the refrigerant switching valve 60 can perform the functions and operations described in the first to fifth embodiments, in other words, the refrigerant switching valve 60 satisfies the configuration of the refrigerant switching valve described in the claims. The configuration of the valve 60 may employ a configuration other than the configurations described in the first to fifth embodiments.

  2. In the first to fifth embodiments, the case where the valve body 80 of the refrigerant switching valve 60 is rotated is illustrated. However, if the opening and closing of the valve body 80 can be performed, the present invention is not limited to rotation, and a straight line It is good also as movements other than rotation, such as a motion. In addition, when rotating the valve body 80 described above, the operation reliability is high, and the configuration can be simple and compact. Therefore, the configuration in which the valve body 80 described is rotated is desirable.

  3. In the first to fifth embodiments, the refrigerant switching valve 60 that controls the flow of the refrigerant is illustrated as the switching valve. However, a switching valve that controls the flow of other circulating media may be used.

  4). In the first to fifth embodiments, the rotation of the rotor is configured to decelerate and rotate the valve body via the pinion gear and the idler gear. However, the rotor and the valve body are not directly decelerated without the idler gear. And the structure which transmits rotation of a rotor directly to a valve body may be sufficient.

  5. In the said 1st-5th embodiment, although the refrigerator was illustrated as an apparatus, of course, you may apply to apparatuses other than a refrigerator.

While various embodiments of the present invention have been described above, various modifications and changes can be made within the scope of the present invention. That is, the specific form of the present invention can be arbitrarily changed as appropriate without departing from the spirit of the invention.

1 Refrigerator (equipment)
1H2 Opening edge 7 Cooler (evaporator)
17 Condensation prevention piping (refrigerant distribution part)
51 Compressor 52 Condenser 54 Pressure reducing means 60 Refrigerant switching valve 66 Valve case (case)
67 Valve seat plate 67a First valve seat plate 67b Second valve seat plate (valve seat)
67c Third valve seat plate (outer valve seat plate)
68 Inflow pipe 69 Communication pipe (1st communication pipe, 2nd communication pipe, 3rd communication pipe)
69b Communication pipe (first communication pipe)
69c Communication pipe (second communication pipe)
69d Communication pipe (3rd communication pipe)
71 Valve body shaft 80 Valve body 81 Valve body sliding contact surface 82 Communication recess (communication groove)
86 Leaf spring (biasing means)
87 Communication tube hole (Communication tube connection part, 1st communication port, 2nd communication port, 3rd communication port)
88 communication holes (communication pipe connection, first communication port, second communication port, third communication port)
89 Inflow pipe hole 90 Polished surface 91 Square 92 Valve body shaft 93 Rotor shaft 94 Widened portion 95 Pressure contact portion 96 Clearance 97 Convex amount 98 Welded portion A Inflow port (inflow tube connection portion)
B communication port (communication pipe connection, first communication port)
C Communication port (communication pipe connection, second communication port)
D Communication port (communication pipe connection, third communication port)

Claims (2)

The disc,
A valve case having an open end covering the valve body;
A valve seat plate provided at one end of the valve case;
With
The valve seat plate is
A first valve seat plate portion;
An outer peripheral valve seat plate portion provided on the outer periphery of the first valve seat plate portion and thinner than the first valve seat plate portion,
The valve case includes an enlarged portion formed by bending R toward the opening side,
The height of the front Symbol step formed between the outer peripheral valve seat plate portion and the first valve seat plate portion is larger than the thickness of the outer peripheral valve seat plate portions,
While the enlarged portion is located within the height dimension of the step,
The inner peripheral surface of the portion formed above the enlarged portion of the valve case is fitted with the step formed on the outer peripheral surface of the first valve seat plate portion, thereby the valve case and The first valve seat plate portion is positioned;
A refrigerant switching valve, wherein welded portions are formed on an outer periphery of the valve case and an outer periphery of the outer peripheral valve seat plate portion.   An apparatus comprising the refrigerant switching valve according to claim 1.