Patent Description:
In a known refrigeration apparatus including a refrigerant circuit for carrying out a vapor compression refrigeration cycle operation, refrigerant pipes through which a refrigerant flows have been integrated into one unit in order to reduce the size of the refrigerant circuit. For example, <CIT>, forming the basis for the preamble of claim <NUM>, discloses a refrigerant pipe unit including three plates that are stacked on top of each other. In this refrigerant pipe unit, a refrigerant flow path is defined between two of the stacked plates, and a valve body, such as an expansion valve or an electromagnetic valve, for controlling the flow of the refrigerant is inserted in one of the plates. <CIT> discloses a vaned spool type directional control valve used to change a direction of motion of an actuator, and including a valve portion and a vane portion integrally formed on a spool shaft.

According to the refrigerant pipe unit disclosed in Patent Literature <NUM>, the valve body is inserted in one of the plates and is configured to move, by linear motion, between a position to narrow the refrigerant flow path and a position to open the refrigerant flow path; therefore, this plate requires a space for allowing the valve body to move linearly. Consequently, the refrigerant pipe unit disclosed in Patent Literature <NUM> is less likely to achieve a size reduction in a direction in which the valve body moves.

An object of the present invention is to provide a compact refrigerant pipe unit and a refrigeration apparatus including the same.

As used therein, the term "to change a flow of a refrigerant" refers to, for example, adjusting a flow rate of the refrigerant or switching a flow direction of the refrigerant.

In the refrigerant pipe unit having the configuration described above, the valve body of the control valve includes the refrigerant passage, and the flow of the refrigerant at the refrigerant flow path changes by a rotation of the valve body. This configuration therefore eliminates or considerably reduces a movement of the valve body in changing the flow of the refrigerant (e.g., a linear movement in a radial direction or along an axial center of rotation of the valve body). As a result, the first plate has almost no necessity to ensure a space that allows the movement of the valve body. This configuration thus achieves a reduction in size of the refrigerant pipe unit.

The refrigerant passage extends in a direction perpendicular to an axial center of rotation of the valve body.

The valve body has an axial center of rotation extending in parallel with a normal direction of the first plate.

An inlet-side refrigerant flow path through which the refrigerant flows into the refrigerant passage in the valve body and an outlet-side refrigerant flow path through which the refrigerant flows out of the refrigerant passage in the valve body is arranged in a linear or planar form in a direction crossing the axial center of rotation of the valve body. This configuration thus achieves a reduction in size of the refrigerant pipe unit in the normal direction of the first plate.

(<NUM>) Preferably, the first plate includes a first accommodation space communicating with the refrigerant flow path.

The valve body is accommodated in the first accommodation space.

The first plate is provided with a first valve seat that is in contact with the valve body in the first accommodation space.

According to this configuration, the valve body is directly disposed in the first plate. Therefore, the control valve can be constituted of the valve seat disposed in the first plate, the valve body, and the driver. This configuration also achieves a reduction in size of the refrigerant pipe unit.

(<NUM>) Preferably, the valve body has a cylindrical shape or a conical shape.

According to this configuration, the valve body is easily accommodated in the accommodation space from the outside of the first plate. It should be noted that the term "conical shape" involves a truncated cone shape corresponding to a conical shape from which a leading end is cut.

(<NUM>) Preferably, the first valve seat includes a sealing member disposed in the first plate.

This configuration ensures hermeticity between the valve body and the first valve seat corresponding to the sealing member and therefore inhibits leakage of the refrigerant.

(<NUM>) Preferably, the second plate includes a second accommodation space communicating with the refrigerant flow path.

The valve body is accommodated in the first accommodation space and the second accommodation space so as to extend over the first accommodation space and the second accommodation space.

The second plate is provided with a second valve seat that is in contact with the valve body in the second accommodation space.

(<NUM>) Preferably, the refrigerant pipe unit further includes.

This configuration allows the refrigerant pipe unit to have a function of controlling multiple flows of the refrigerant.

<FIG> is a diagram of a schematic configuration of a refrigeration apparatus to which a refrigerant pipe unit according to a first embodiment of the present invention is applied.

The refrigeration apparatus <NUM> is, for example, an air conditioner for cooling and heating air in a room. The refrigeration apparatus <NUM> includes an outdoor unit <NUM> installed outside the room, and an indoor unit <NUM> installed in the room. The outdoor unit <NUM> and the indoor unit <NUM> are connected to each other with a refrigerant pipe <NUM>. The refrigeration apparatus <NUM> may include a single indoor unit <NUM> or may include a plurality of indoor units <NUM>.

The refrigeration apparatus <NUM> includes a refrigerant circuit <NUM> for carrying out a vapor compression refrigeration cycle operation. The refrigerant circuit <NUM> includes an indoor heat exchanger <NUM>, a compressor <NUM>, a supercooler <NUM>, an outdoor heat exchanger <NUM>, an outdoor expansion valve <NUM>, an accumulator <NUM>, a four-way switching valve <NUM>, shutoff valves <NUM> and <NUM>, an oil separator <NUM>, an indoor expansion valve <NUM>, and the like which are connected to each other with the refrigerant pipe <NUM>.

Among the constituent components of the refrigerant circuit <NUM>, the indoor heat exchanger <NUM> and the indoor expansion valve <NUM> are of the indoor unit <NUM>. Among the constituent components of the refrigerant circuit <NUM>, the compressor <NUM>, the supercooler <NUM>, the outdoor heat exchanger <NUM>, the outdoor expansion valve <NUM>, the accumulator <NUM>, the four-way switching valve <NUM>, the shutoff valves <NUM> and <NUM>, and the oil separator <NUM> are of the outdoor unit <NUM>.

During a cooling operation carried out by the air conditioner <NUM>, the four-way switching valve <NUM> is switched to a state indicated by a solid line illustrated in <FIG>, and the outdoor heat exchanger <NUM> functions as a refrigerant condenser (radiator) while the indoor heat exchanger <NUM> functions as a refrigerant evaporator. The gas-state refrigerant discharged from the compressor <NUM> passes through the oil separator <NUM> and then flows into the outdoor heat exchanger <NUM>. The oil separator <NUM> separates a refrigerating machine oil contained in the gas-state refrigerant, from the gas-state refrigerant. The outdoor heat exchanger <NUM> condenses the gas-state refrigerant into the liquid-state refrigerant by heat exchange with outside air. The liquid-state refrigerant then flows into the supercooler <NUM> via the outdoor expansion valve <NUM>. The supercooler <NUM> cools the refrigerant condensed by the outdoor heat exchanger <NUM>. After passing through the supercooler <NUM>, the refrigerant is decompressed at the indoor expansion valve <NUM>. The indoor heat exchanger <NUM> then evaporates the refrigerant by heat exchange with indoor air. The refrigerant then passes through the accumulator <NUM>. The refrigerant is then sucked into the compressor <NUM>. The accumulator <NUM> separates the gas-state refrigerant and the liquid-state refrigerant from each other. Only the gas-state refrigerant is sucked into the compressor <NUM>.

The supercooler <NUM> includes a main flow path 13e and an auxiliary flow path 13f. The main flow path 13e includes a first end communicating with a first port 13a of the supercooler <NUM>. The supercooler <NUM> is connected at the first port 13a to a refrigerant pipe 10a extending from the outdoor heat exchanger <NUM>. The main flow path 13e includes a second end communicating with a second port 13b of the supercooler <NUM>. The supercooler <NUM> is connected at the second port 13b to a refrigerant pipe 10b extending to the indoor heat exchanger <NUM>.

The auxiliary flow path 13f includes a first end communicating with a third port 13c of the supercooler <NUM>. The supercooler <NUM> is connected at the third port 13c to a refrigerant pipe 10c branching off the refrigerant pipe 10a. The refrigerant pipe 10c is provided with a supercooling expansion valve <NUM>. The auxiliary flow path 13f includes a second end communicating with a fourth port 13d of the supercooler <NUM>. The supercooler <NUM> is connected at the fourth port 13d to a refrigerant pipe 10d extending to the accumulator <NUM>. The refrigerant pipe 10d is provided with an open-close valve <NUM>. In the supercooler <NUM>, the high-pressure liquid refrigerant flowing from the outdoor heat exchanger <NUM> to the main flow path 13e exchanges heat with the low-pressure gas-liquid two-phase refrigerant decompressed at the supercooling expansion valve <NUM> and flowing through the auxiliary flow path 13f.

The refrigeration apparatus <NUM> according to the present invention includes a refrigerant pipe unit <NUM> that includes one or more constituent components and refrigerant flow paths connected to and integrated with the constituent components. The refrigerant pipe unit <NUM> according to the present embodiment includes the outdoor expansion valve <NUM>, four-way switching valve <NUM>, supercooling expansion valve <NUM>, and open-close valve <NUM> as the constituent components, and some of the refrigerant pipes connected to the constituent components.

Specifically, the refrigerant pipe unit <NUM> includes a first flow path <NUM>, a second flow path <NUM>, a third flow path <NUM>, and a fourth flow path <NUM>. The first to fourth flow paths <NUM> to <NUM> are connected to the four-way switching valve <NUM>. The first flow path <NUM> includes a first end 31a connected to a first port 17a of the four-way switching valve <NUM>, and a second end 31b connected to a refrigerant pipe extending to the oil separator <NUM>. The second flow path <NUM> includes a first end 32a connected to a second port 17b of the four-way switching valve <NUM>, and a second end 32b connected to a refrigerant pipe extending to the outdoor heat exchanger <NUM>.

The third flow path <NUM> includes a first end 33a connected to a third port 17c of the four-way switching valve <NUM>, and a second end 33b connected to a refrigerant pipe extending to the accumulator <NUM>. The fourth flow path <NUM> includes a first end 34a connected to a fourth port 17d of the four-way switching valve <NUM>, and a second end 34b connected to a refrigerant pipe extending to the gas-side shutoff valve <NUM>.

The refrigerant pipe unit <NUM> also includes a fifth flow path <NUM>, a sixth flow path <NUM>, a seventh flow path <NUM>, an eighth flow path <NUM>, a ninth flow path <NUM>, and a tenth flow path <NUM>. The fifth to tenth flow paths <NUM> to <NUM> are connected to the outdoor expansion valve <NUM>, the supercooling expansion valve <NUM>, and the open-close valve <NUM>. The fifth flow path <NUM> includes a first end 35a connected to a first port 15a of the outdoor expansion valve <NUM>, and a second end 35b connected to a refrigerant pipe extending to the outdoor heat exchanger <NUM>. The sixth flow path <NUM> includes a first end 36a connected to a second port 15b of the outdoor expansion valve <NUM>, and a second end 36b connected to a refrigerant pipe extending to the first port 13a of the supercooler <NUM>.

The seventh flow path <NUM> includes a first end 37a connected to a midway portion between two ends of the sixth flow path <NUM>, and a second end 37b connected to a first port 21a of the supercooling expansion valve <NUM>. The eighth flow path <NUM> includes a first end 38a connected to a second port 21b of the supercooling expansion valve <NUM>, and a second end 38b connected to a refrigerant pipe extending to the third port 13c of the supercooler <NUM>.

The ninth flow path <NUM> includes a first end 39a connected to a first port 22a of the open-close valve <NUM>, and a second end 39b connected to a refrigerant pipe extending to the fourth port 13d of the supercooler <NUM>. The tenth flow path <NUM> includes a first end 40a connected to a second port 22b of the open-close valve <NUM>, and a second end 40b connected to a midway portion between two ends of the third flow path <NUM>. A refrigerant pipe 10e for injection includes a first end connected to the compressor <NUM>, and the refrigerant having an intermediate pressure between a suction pressure and a discharge pressure is introduced into the compressor <NUM> through the refrigerant pipe 10e. The refrigerant pipe 10e includes a second end connected to a midway portion between two ends of the refrigerant pipe connecting the second end 39b of the ninth flow path <NUM> and the fourth port 13d of the supercooler <NUM>. When the open-close valve <NUM> is closed, the intermediate-pressure refrigerant is supplied to the compressor <NUM> through the refrigerant pipe 10e.

Next, a description will be given of a specific structure of the refrigerant pipe unit <NUM>. <FIG> is a perspective view of the refrigerant pipe unit.

The refrigerant pipe unit <NUM> includes a unit main body <NUM> and control valves <NUM>, <NUM>, <NUM>, and <NUM>. The unit main body <NUM> includes a plurality of plates <NUM> to <NUM> stacked on top of each other. The unit main body <NUM> has a flow path through which the refrigerant flows and that is defined in the unit main body <NUM>.

The unit main body <NUM> includes the first plate <NUM>, the second plate <NUM>, the third plate <NUM>, and the fourth plate <NUM>. Each of the first plate <NUM>, the second plate <NUM>, and the fourth plate <NUM> is a plate member having a rectangular shape, a square shape, or the like. The first plate <NUM>, the second plate <NUM>, and the fourth plate <NUM> are equal in outer dimension to one another. Each of the plates <NUM> to <NUM> is made of metal such as aluminum, an aluminum alloy, or stainless steel. The first plate <NUM>, the second plate <NUM>, and the fourth plate <NUM> are stacked in this order and joined together by brazing. The unit main body <NUM> therefore includes a brazing portion for joining the plates <NUM>, <NUM>, and <NUM> together.

The first plate <NUM>, the second plate <NUM>, and the fourth plate <NUM> are different in thickness from one another. The first plate <NUM> is thicker than the second to fourth plates <NUM> to <NUM>. The second plate <NUM> is thicker than the third plate <NUM> and the fourth plate <NUM>.

The unit main body <NUM> includes a plurality of third plates <NUM>. Each of the third plates <NUM> is a plate member having a rectangular shape or a square shape. Each of the third plates <NUM> is smaller in outer dimension than the first plate <NUM> and is stacked on the first plate <NUM>. The unit main body <NUM> according to the present embodiment includes four third plates <NUM>. Each of the third plates <NUM> is joined to the first plate <NUM> by welding. The unit main body <NUM> therefore includes a welding portion for joining the first plate <NUM> and each third plate <NUM> together. In the present embodiment, the term "welding" refers to welding that involves melting of a base material.

The unit main body <NUM> is manufactured as follows. First, the first plate <NUM>, second plate <NUM>, and fourth plate <NUM> of the unit main body <NUM> are joined together by brazing and integrated into one in a furnace. Next, three valve seats <NUM> and one valve seat <NUM> as well as three valve bodies <NUM> and one valve body <NUM> (to be described later) for the control valves <NUM>, <NUM>, <NUM>, and <NUM> are respectively inserted into three accommodation holes 51j and one accommodation hole <NUM> in the first plate <NUM>, and the accommodation holes 51j and <NUM> as well as the flow paths <NUM> to <NUM> are closed with the third plates <NUM>. Thereafter, the third plates <NUM> and the first plate <NUM> are joined together by welding. By this manufacturing method, the first, second, and fourth plates <NUM>, <NUM>, and <NUM>, which are less susceptible to a thermal influence, can be brazed collectively and, after the brazing, the control valves <NUM>, <NUM>, <NUM>, and <NUM>, which are susceptible to a thermal influence, can be mounted to the first plate <NUM>; therefore, the manufacturability can be improved.

In the following description, a first direction Z may refer to a direction in which the first to fourth plates <NUM> to <NUM> are stacked (i.e., a normal direction of each of the first to fourth plates <NUM> to <NUM>), and a second direction X and a third direction Y each may refer to a direction orthogonal to the first direction Z. In the present embodiment, the refrigerant pipe unit <NUM> is placed with the first direction Z oriented in a heightwise direction.

<FIG> is an exploded perspective view of the refrigerant pipe unit. <FIG> is a diagram illustrating an internal structure of the refrigerant pipe unit. <FIG> is a sectional view of the refrigerant pipe unit, taken along line A-A in <FIG>.

The unit main body <NUM> includes the first to tenth flow paths <NUM> to <NUM> as described above. Specifically, the first plate <NUM> includes the first to tenth flow paths <NUM> to <NUM>. The first to tenth flow paths <NUM> to <NUM> pass through the first plate <NUM> in the first direction Z. Each of the first to tenth flow paths <NUM> to <NUM> has a substantially square shape as seen in the first direction Z.

The first to fourth flow paths <NUM> to <NUM> are arranged in the second direction X and the third direction Y on a first side of the first plate <NUM> in the second direction X (i.e., the right side in <FIG>). The first flow path <NUM> and the second flow path <NUM> are arranged in the third direction Y and are separated from each other with a first partition wall 51a interposed therebetween. The second flow path <NUM> and the third flow path <NUM> are arranged in the second direction X and are separated from each other with a second partition wall 51b interposed therebetween. The third flow path <NUM> and the fourth flow path <NUM> are arranged in the third direction Y and are separated from each other with a third partition wall 51c interposed therebetween. The fourth flow path <NUM> and the first flow path <NUM> are arranged in the second direction X and are separated from each other with a fourth partition wall 51d interposed therebetween.

The accommodation hole (accommodation space) <NUM> is located at an intersection of the first partition wall 51a, the second partition wall 51b, the third partition wall 51c, and the fourth partition wall 51d, and passes through the first plate <NUM> in the first direction Z. The accommodation hole <NUM> accommodates therein the valve body <NUM> of the second control valve <NUM> as will be described later. The accommodation hole <NUM> has a cylindrical inner peripheral surface.

The fifth to tenth flow paths <NUM> to <NUM> are arranged in the second direction X and the third direction Y on a second side of the first plate <NUM> in the second direction X (i.e., the left side in <FIG>). The fifth flow path <NUM> and the sixth flow path <NUM> are arranged in the second direction X and are separated from each other with a fifth partition wall 51e interposed therebetween. The seventh flow path <NUM> and the eighth flow path <NUM> are arranged in the second direction X and are separated from each other with a sixth partition wall 51f interposed therebetween. The seventh flow path <NUM> includes a first portion 37c defined in the first plate <NUM> and a second portion 37d defined in the second plate <NUM>, as will be described later.

The ninth flow path <NUM> and the tenth flow path <NUM> are arranged in the second direction X and are separated from each other with a seventh partition wall <NUM> interposed therebetween. The tenth flow path <NUM> includes a first portion 40c defined in the first plate <NUM> and a second portion 40d defined in the second plate <NUM>, as will be described later. The fifth flow path <NUM>, the eighth flow path <NUM>, and the ninth flow path <NUM> are arranged in this order in the third direction Y. The sixth flow path <NUM>, the seventh flow path <NUM>, and the tenth flow path <NUM> are arranged in this order in the third direction Y.

The fifth partition wall 51e, sixth partition wall 51f, and seventh partition wall <NUM> respectively have the accommodation holes (accommodation spaces) 51j each passing through the first plate <NUM> in the first direction Z. The accommodation holes 51j respectively accommodate therein the valve bodies <NUM> of the first control valves <NUM>, <NUM>, and <NUM> as will be described later. The accommodation holes 51j each have a cylindrical inner peripheral surface.

As illustrated in <FIG>, the seventh flow path <NUM> is defined in not only the first plate <NUM>, but also the second plate <NUM>. As described above, the seventh flow path <NUM> includes the first portion 37c defined in the first plate <NUM> and the second portion 37d defined in the second plate <NUM>. The second portion 37d passes through the second plate <NUM> in the first direction Z. The second portion 37d is an oblong hole formed longitudinally in the third direction Y. The second portion 37d extends over the sixth flow path <NUM> and the first portion 37c of the seventh flow path <NUM> in the first plate <NUM>, so that the sixth flow path <NUM> and the first portion 37c communicate with each other.

As illustrated in <FIG> and <FIG>, the tenth flow path <NUM> is defined in not only the first plate <NUM>, but also the second plate <NUM>. As described above, the tenth flow path <NUM> includes the first portion 40c defined in the first plate <NUM> and the second portion 40d defined in the second plate <NUM>. The second portion 40d is an oblong hole formed longitudinally in the second direction X. The second portion 40d extends over the first portion 40c of the tenth flow path <NUM> and the third flow path <NUM> in the first plate, so that the first portion 40c and the third flow path <NUM> communicate with each other.

As illustrated in <FIG>, <FIG>, and <FIG>, the four third plates <NUM> close the first to tenth flow paths <NUM> to <NUM> from above. Specifically, the four third plates <NUM> respectively close the first to fourth flow paths <NUM> to <NUM>, fifth and sixth flow paths <NUM> and <NUM>, seventh and eighth flow paths <NUM> and <NUM>, and ninth and tenth flow paths <NUM> and <NUM>.

As illustrated in <FIG>, the third plates <NUM> have through holes that define the second ends 31b to 36b of the first to sixth flow paths <NUM> to <NUM> as well as the second ends 38b and 39b of the eighth and ninth flow paths <NUM> and <NUM> (see <FIG>). The refrigerant pipes are respectively connected to the through holes. Drivers <NUM> (to be described later) that constitute the control valves are respectively disposed on the third plates <NUM>.

As illustrated in <FIG>, the fourth plate <NUM> is located below the second plate <NUM>. The fourth plate <NUM> has no opening and closes the second portion 37d of the seventh flow path <NUM> and the second portion 40d of the tenth flow path <NUM> in the second plate <NUM> from below.

As illustrated in <FIG> and <FIG>, the control valves <NUM>, <NUM>, <NUM>, and <NUM> are configured to control a flow of the refrigerant in the unit main body <NUM>. The refrigerant pipe unit <NUM> according to the present embodiment includes, as the control valves, the outdoor expansion valve <NUM>, supercooling expansion valve <NUM>, open-close valve <NUM>, and four-way switching valve <NUM> described above with reference to <FIG>. Each of the outdoor expansion valve <NUM>, the supercooling expansion valve <NUM>, and the open-close valve <NUM> is a flow rate adjustment valve configured to adjust a flow rate of the refrigerant. In the following description, a first control valve refers to this flow rate adjustment valve. The four-way switching valve <NUM> is a direction switching valve configured to switch a flow direction of the refrigerant. In the following description, a second control valve refers to this direction switching valve.

Each of the outdoor expansion valve <NUM> and the supercooling expansion valve <NUM> adjusts an opening degree of its corresponding valve body between a minimum opening degree and a maximum opening degree continuously or stepwise to adjust the flow rate of the refrigerant. The open-close valve <NUM> switches the opening degree of its valve body to either the maximum opening degree or the minimum opening degree (fully closed), thereby adjusting the flow rate of the refrigerant. In other words, the open-close valve <NUM> switches between a form of interrupting the flow of the refrigerant and a form of permitting the flow of the refrigerant.

Each of the outdoor expansion valve <NUM>, the supercooling expansion valve <NUM>, the open-close valve <NUM>, and the four-way switching valve <NUM> is an electric valve operable by power supply. The valves <NUM>, <NUM>, and <NUM> respectively include the valve bodies <NUM> and the drivers <NUM>. The valve <NUM> includes the valve body <NUM> and the driver <NUM>. The valve bodies <NUM> and <NUM> are disposed in the unit main body <NUM>. The drivers <NUM> are disposed outside the unit main body <NUM>.

<FIG> is an exploded perspective view illustrating a part of the first control valve in the refrigerant pipe unit. <FIG> is an exploded perspective view illustrating a part of the second control valve in the refrigerant pipe unit. <FIG> is a sectional view of the first control valve. It should be noted that <FIG> and <FIG> each illustrate, as an example, the outdoor expansion valve <NUM> among the plurality of first control valves <NUM>, <NUM>, and <NUM>. The outdoor expansion valve <NUM>, supercooling expansion valve <NUM>, and open-close valve <NUM> are basically equal in structure to each other. In the following, therefore, a description will be given of a specific structure of the outdoor expansion valve <NUM> as an example.

As illustrated in <FIG>, the valve body <NUM> of the outdoor expansion valve <NUM> has a cylindrical (columnar) shape. The valve body <NUM> has a height in the first direction Z, and this height is substantially equal to a thickness of the first plate <NUM>. The valve body <NUM> has an opening 43a passing through the valve body <NUM> in a direction parallel to a direction perpendicular to an axial center C1 of the valve body <NUM>. The opening 43a crosses the axial center C1 of the valve body <NUM>. The opening 43a serves as a passage through which the refrigerant flows. The valve body <NUM> includes a cylindrical projection 43b disposed on an upper surface of the valve body <NUM> and located on the axial center C1. The projection 43b has on its upper surface a groove 43b1 extending in a radial direction of the projection 43b.

The valve body <NUM> is accommodated in the accommodation hole (accommodation space) 51j bored in the first plate <NUM>. The axial center C1 of the valve body <NUM> extends in parallel with the first direction Z which is the normal direction of the first plate <NUM>. The axial center C1 of the valve body <NUM> is aligned with a center of the accommodation hole 51j.

The first plate <NUM> has openings located around the accommodation hole 51j and serving as the first port 15a and second port 15b of the outdoor expansion valve <NUM>. The first port 15a allows the accommodation hole 51j and the flow path <NUM> to communicate with each other. The second port 15b allows the accommodation hole 51j and the flow path <NUM> to communicate with each other. The first port 15a and the second port 15b are substantially equal in area to the opening 43a in the valve body <NUM>.

The first plate <NUM> is provided with the valve seat <NUM> that is in contact with the valve body <NUM>. The valve seat <NUM> is made of a synthetic resin and has a cylindrical shape. The valve seat <NUM> has a height in the first direction Z, and this height is substantially equal to the thickness of the first plate <NUM> in the first direction Z. The valve seat <NUM> has an axial center aligned with the axial center C1 of the valve bodies <NUM>. In the following, therefore, reference sign C1 indicates the axial center of the valve seat <NUM> in addition to the axial center of the valve body <NUM>.

The valve seat <NUM> has an outer diameter that is substantially equal to or slightly smaller than an inner diameter of the accommodation hole 51j. The valve seat <NUM> also has an inner diameter that is substantially equal or slightly larger than an outer diameter of the valve body <NUM>. The valve seat <NUM> is fitted into the accommodation hole 51j and is fixed to the inner peripheral surface of the accommodation hole 51j. The valve body <NUM> is inserted in the valve seat <NUM> so as to be rotatable about the axial center C1.

The valve seat <NUM> has a pair of openings 46a passing through the valve seat <NUM> in a direction perpendicular to the axial center C1 of the valve seat <NUM>. The openings 46a are arranged at positions displaced by <NUM> degrees in a circumferential direction of the valve seat <NUM>. The openings 46a in the valve seat <NUM> are substantially equal in area to the opening 43a in the valve body <NUM>. The valve seat <NUM> functions as a sealing member that seals a gap between the inner peripheral surface of the accommodation hole 51j and an outer peripheral surface of the valve body <NUM> to inhibit leakage of the refrigerant through the gap.

As illustrated in <FIG>, the valve body <NUM> of the four-way switching valve <NUM> which is also referred to as the second control valve has a cylindrical (columnar) shape, as in the valve body <NUM> of the outdoor expansion valve <NUM>. The valve body <NUM> has a height in the first direction Z, and this height is substantially equal to the thickness of the first plate <NUM>. The valve body <NUM> of the four-way switching valve <NUM> has a pair of openings 44a passing through the valve body <NUM> in a direction parallel to a direction perpendicular to an axial center C2 of the valve body <NUM>. The openings 44a extend in parallel, with the axial center C2 of the valve body <NUM> interposed therebetween. The openings 44a each serve as a passage through which the refrigerant flows. The valve body <NUM> includes a cylindrical projection 44b disposed on an upper surface of the valve body <NUM> and located on the axial center C2. The projection 44b has on its upper surface a groove 44b1 extending in a radial direction of the projection 44b.

The valve body <NUM> is accommodated in the accommodation hole (accommodation space) <NUM> bored in the first plate <NUM>. The axial center C2 of the valve body <NUM> extends in parallel with the first direction Z which is the normal direction of the first plate <NUM>. The axial center C2 of the valve body <NUM> is aligned with a center of the accommodation hole <NUM>.

The first plate <NUM> has openings located around the accommodation hole <NUM> and serving as the first port 17a, second port 17b, third port 17c, and fourth port 17d of the four-way switching valve <NUM>. The first port 17a, second port 17b, third port 17c, and fourth port 17d respectively allow the accommodation hole <NUM> and the first flow path <NUM>, second flow path <NUM>, third flow path <NUM>, and fourth flow path <NUM> to communicate with each other. The first port 17a, the second port 17b, the third port 17c, and the fourth port 17d are substantially equal in area to the openings 44a in the valve body <NUM>.

The first plate <NUM> is provided with the valve seat <NUM> that is in contact with the valve body <NUM>. The valve seat <NUM> is made of a synthetic resin and has a cylindrical shape. The valve seat <NUM> has a height in the first direction Z, and this height is substantially equal to the thickness of the first plate <NUM> in the first direction Z. The valve seat <NUM> has an axial center aligned with the axial center C2 of the valve body <NUM>. In the following, therefore, reference sign C2 indicates the axial center of the valve seat <NUM> in addition to the axial center of the valve body <NUM>.

The valve seat <NUM> has an outer diameter that is substantially equal to or slightly smaller than an inner diameter of the accommodation hole <NUM>. The valve seat <NUM> also has an inner diameter that is substantially equal or slightly larger than an outer diameter of the valve body <NUM>. The valve seat <NUM> is fitted into the accommodation hole <NUM> and is fixed to the inner peripheral surface of the accommodation hole <NUM>. The valve body <NUM> is inserted in the valve seat <NUM> so as to be rotatable about the axial center C1.

The valve seat <NUM> has four openings 47a passing through the valve seat <NUM> in a direction perpendicular to the axial center C2 of the valve seat <NUM>. The four openings 47a are spaced away from one another at equal intervals (<NUM>-degree intervals) in a circumferential direction of the valve seat <NUM>. The openings 47a in the valve seat <NUM> are substantially equal in area to the openings 44a in the valve body <NUM>. The openings 47a in the valve seat <NUM> are coincide in circumferential position with and communicate with the first port 17a, second port 17b, third port 17c, and fourth port 17d in the first plate <NUM>, respectively. The valve seat <NUM> functions as a sealing member that seals a gap between the inner peripheral surface of the accommodation hole <NUM> and an outer peripheral surface of the valve body <NUM> to inhibit leakage of the refrigerant through the gap.

As illustrated in <FIG>, the driver <NUM> of the outdoor expansion valve <NUM> is constituted of an electric motor such as a stepping motor. The driver <NUM> includes a rotor 45a, a stator 45b, and a cover 45c. The stator 45b includes a coil 45b1. The rotor 45a includes a projection 45a1 disposed on a lower end of the rotor 45a. The projection 45a1 of the rotor 45a is inserted in the groove 43b1 in the projection 43b of the valve body <NUM>. The projection 45a1 of the rotor 45a and the projection 43b of the valve body <NUM> thus engage with each other, so that the rotor 45a and the valve body <NUM> are integrally rotatable about the axial center C1.

The cover 45c is a plate member made of metal such as aluminum, an aluminum alloy, or stainless steel. The cover 45c has a cylindrical shape with its upper end closed, and covers an outer peripheral portion and an upper portion of the rotor 45a. The cover 45c is integrated with the third plate <NUM>. The stator 45b covers an outer peripheral portion and an upper portion of the cover 45c. The cover 45c may alternatively be provided separately from the third plate <NUM>.

The driver <NUM> rotates the valve body <NUM> about the axial center C1 at a desired rotational angle in such a manner that the stator 45b excited by energization to the coil 45b1 rotates the rotor 45a. The valve body <NUM> changes, in accordance with its amount of rotation, a flow rate of the refrigerant flowing through the opening 43a, and accordingly changes a flow of the refrigerant in the flow paths <NUM> and <NUM> of the unit main body <NUM> communicating with the opening 43a. The four-way switching valve <NUM>, which is the second control valve, also includes a driver <NUM> similar in configuration to the driver <NUM> of the outdoor expansion valve <NUM>.

<FIG> are diagrams each illustrating action of the first control valve.

The outdoor expansion valve <NUM>, which is the first control valve, has an opening degree adjusted by a rotation of the valve body <NUM> to one of a state of a maximum opening degree (fully open) illustrated in <FIG>, a state of a minimum opening degree (fully closed) illustrated in <FIG>, and a state of an intermediate opening degree illustrated in <FIG>. At the intermediate opening degree, the amount of rotation of the valve body <NUM> is adjusted continuously or stepwise. The outdoor expansion valve <NUM> is capable of adjusting the flow rate of the refrigerant flowing through the flow paths <NUM> and <NUM>, based on the adjustment to its opening degree.

The supercooling expansion valve <NUM>, which is similar to the outdoor expansion valve <NUM>, also has an opening degree adjusted by the rotation of the valve body <NUM> to one of a state of a maximum opening degree, a state of a minimum opening degree, and a state of an intermediate opening degree.

On the other hand, the open-close valve <NUM> has an opening degree adjusted to one of the state of the maximum opening degree illustrated in <FIG> and the state of the minimum opening degree illustrated in <FIG>. The adjustment to the opening degree enables switching between the form of permitting the flow of the refrigerant in the flow paths <NUM> and <NUM> and the form of interrupting the flow of the refrigerant in the flow paths <NUM> and <NUM>.

<FIG> are diagrams each illustrating action of the second control valve.

The four-way switching valve <NUM>, which is the second control valve, switches, by a rotation of the valve body <NUM>, a flow direction of the refrigerant to one of a state in which the first flow path <NUM> communicates with the second flow path <NUM> while the third flow path <NUM> communicates with the fourth flow path <NUM> as illustrated in <FIG> and a state in which the first flow path <NUM> communicates with the fourth flow path <NUM> while the second flow path <NUM> communicates with the third flow path <NUM> as illustrated in <FIG>. The switching of the flow direction enables switching between a cooling operation and a heating operation by the air conditioner <NUM>.

According to the first embodiment described above, the refrigerant pipe unit <NUM> includes the plurality of control valves <NUM>, <NUM>, <NUM>, and <NUM>, and the control valves <NUM>, <NUM>, <NUM>, and <NUM> include the valve bodies <NUM> and <NUM> disposed on the first plate <NUM> in a rotatable manner. The valve bodies <NUM> and <NUM> respectively have the openings 43a and 44a each serving as a refrigerant passage. The valve bodies <NUM> and <NUM> change the flow of the refrigerant in the flow paths <NUM> to <NUM>, in accordance with their amounts of rotation. The valve bodies <NUM> and <NUM> respectively rotate about the axial centers C1 and C2 extending in parallel with the normal direction Z of the first plate <NUM>. The openings 43a and 44a are defined along the direction orthogonal to the axial centers C1 and C2. Therefore, the inlet-side flow paths through which the refrigerant flows into the openings 43a and 44a in the valve bodies <NUM> and <NUM> and the outlet-side flow paths through which the refrigerant flows out of the openings 43a and 44a can be arranged linearly, which enables a reduction in space for these flow paths.

The valve bodies <NUM> of the first control valves <NUM>, <NUM>, and <NUM> are respectively accommodated in the accommodation spaces 51j in the first plate <NUM> and are respectively in contact with the valve seats <NUM> of the first plate <NUM>. The valve body <NUM> of the second control valve <NUM> is accommodated in the accommodation space <NUM> in the first plate <NUM> and is in contact with the valve seat <NUM> of the first plate <NUM>. The first plate <NUM> therefore functions as a casing for the first control valves <NUM>, <NUM>, and <NUM> and the second control valve <NUM>. This configuration thus achieves a reduction in size of the refrigerant pipe unit <NUM>.

In the foregoing embodiment, the outdoor expansion valve <NUM>, supercooling expansion valve <NUM>, and open-close valve <NUM> include the valve bodies <NUM> of the same type and the valve seats <NUM> of the same type. This configuration therefore achieves a reduction in manufacturing cost by the use of common components.

In the foregoing embodiment, control valves of different types can be configured with ease by changing the structures of valve bodies to be accommodated in the accommodation spaces <NUM> and 51j. Any of the accommodation holes <NUM> and 51j may accommodate therein components different from a valve body, such as a filter.

<FIG> is a perspective view of a refrigerant pipe unit according to a second embodiment of the present invention.

A refrigerant pipe unit <NUM> according to the present embodiment includes a unit main body <NUM> and control valves <NUM>, <NUM>, and <NUM>.

As in the first embodiment, the unit main body <NUM> includes a plurality of plates <NUM> to <NUM> stacked on top of each other. The unit main body <NUM> has a flow path through which a refrigerant flows and that is defined in the unit main body <NUM>.

The unit main body <NUM> includes the first plate <NUM>, the second plate <NUM>, the third plate <NUM>, the fourth plate <NUM>, and the fifth plate <NUM>. Each of the first plate <NUM>, the second plate <NUM>, the fourth plate <NUM>, and the fifth plate <NUM> is a plate member having a rectangular shape, a square shape, or the like. The first plate <NUM>, the second plate <NUM>, the fourth plate <NUM>, and the fifth plate <NUM> are equal in outer dimension to one another. The first plate <NUM>, the second plate <NUM>, the fourth plate <NUM>, and the fifth plate <NUM> are stacked in this order and joined together by brazing. The unit main body <NUM> therefore includes a brazing portion for joining the plates <NUM>, <NUM>, <NUM>, and <NUM> together.

The first plate <NUM> is substantially equal in thickness to the second plate <NUM>. The third plate <NUM>, the fourth plate <NUM>, and the fifth plate <NUM> are different in thickness from the first plate <NUM> and the second plate <NUM>. The fourth plate <NUM> is thicker than the first plate <NUM> and the second plate <NUM>. The third plate <NUM> and the fifth plate <NUM> are thinner than the first plate <NUM>.

The unit main body <NUM> includes a plurality of third plates <NUM>. The third plates <NUM> have sizes that respectively cover valve bodies (to be described later) and flow paths (to be described later) through which the refrigerant flows. Each of the third plates <NUM> is smaller in outer dimension than the first plate <NUM> and is stacked on the first plate <NUM>. The unit main body <NUM> according to the present embodiment includes eleven third plates <NUM>. Each of the third plates <NUM> is joined to the first plate <NUM> by welding. The unit main body <NUM> therefore includes a welding portion for joining the first plate <NUM> and each third plate <NUM> together. The first plate <NUM> has a plurality of holes <NUM> through which refrigerant pipes are connected to the flow paths in the unit main body <NUM>.

<FIG> is a plan view of a second control valve.

A second control valve <NUM> is a direction switching valve. The second control valve <NUM> is a three-way switching valve for adjusting a flow direction of the refrigerant by causing two of three flow paths <NUM>, <NUM>, and <NUM> defined in the first plate <NUM> and the like to selectively communicate with each other.

<FIG> is an exploded perspective view of a part of the second control valve. <FIG> is a sectional view illustrating the second control valve and a refrigerant flow path around the second control valve.

The first plate <NUM> has an accommodation hole (first accommodation space) 71a passing through the first plate <NUM> in the first direction Z. The second plate <NUM> has an accommodation hole (second accommodation space) 72a passing through the second plate <NUM> in the first direction Z. The accommodation holes 71a and 72a each have a cylindrical shape, are equal in inner diameter to each other, and are arranged concentrically. The first plate <NUM> has three flow paths <NUM>, <NUM>, and <NUM> defined around the accommodation hole 71a. The second plate <NUM> has three flow paths <NUM>, <NUM>, and <NUM> defined around the accommodation hole 72a. The flow path <NUM> and the flow path <NUM> are arranged in a circumferential direction of the accommodation holes 71a and 72a so as to face each other at an angle of <NUM> degrees. The flow path <NUM> is arranged in the circumferential direction of the accommodation holes 71a and 72a at an angle of <NUM> degrees relative to the flow path <NUM> and the flow path <NUM>. The flow paths <NUM>, <NUM>, and <NUM> have widths smaller than the diameters of the accommodation holes 71a and 72a as seen in the first direction Z.

The second control valve <NUM> includes a valve body <NUM> and a driver <NUM>. The valve body <NUM> is disposed in the unit main body <NUM>. The driver <NUM> is disposed outside the unit main body <NUM>. The driver <NUM> is equal in configuration to the driver <NUM> described above with reference to, for example, <FIG>; therefore, the detailed description thereof will not be given here.

As illustrated in <FIG>, the valve body <NUM> has a cylindrical (columnar) shape. The valve body <NUM> has a height in the first direction Z, and this height is substantially equal to a sum of a thickness of the first plate <NUM> and a thickness of the second plate <NUM>. The valve body <NUM> has an opening 77a passing through the valve body <NUM> in a direction parallel to a direction perpendicular to an axial center C3 of the valve body <NUM>. The opening 77a crosses the axial center C3 of the valve body <NUM>. The opening 77a serves as a passage through which the refrigerant flows. The opening 77a is biased toward a first side in a radial direction, within a range that covers the axial center C3 of the valve body <NUM>. The valve body <NUM> includes a cylindrical projection 77b disposed on an upper surface of the valve body <NUM> and located on the axial center C3. The projection 77b has on its upper surface a groove 77b1 extending in a radial direction of the projection 77b.

The valve body <NUM> is accommodated in the accommodation holes (accommodation spaces) 71a and 72a respectively bored in the first and second plates <NUM> and <NUM>. The axial center C3 of the valve body <NUM> extends in parallel with the first direction Z which is the normal direction of the first plate <NUM>. The axial center C3 of the valve body <NUM> is aligned with centers of the accommodation holes 71a and 72a.

The first plate <NUM> and the second plate <NUM> are provided with a valve seat <NUM> that is in contact with the valve body <NUM>. The valve seat <NUM> is made of a synthetic resin and has a cylindrical shape. The valve seat <NUM> has a height in the first direction Z, and this height is substantially equal to the sum of the thickness of the first plate <NUM> and the thickness of the second plate <NUM> in the first direction Z. The valve seat <NUM> has an axial center aligned with the axial center C3 of the valve body <NUM>. In the following, therefore, reference sign C3 indicates the axial center of the valve seat <NUM> in addition to the axial center of the valve body <NUM>.

The valve seat <NUM> has an outer diameter that is substantially equal to or slightly smaller than the inner diameters of the accommodation holes 71a and 72a. The valve seat <NUM> also has an inner diameter that is substantially equal or slightly larger than an outer diameter of the valve body <NUM>. The valve seat <NUM> is fitted into the accommodation holes 71a and 72a and is fixed to inner peripheral surfaces of the accommodation holes 71a and 72a. The valve body <NUM> is inserted in the valve seat <NUM> so as to be rotatable about the axial center C3.

The valve seat <NUM> has three openings 79a passing through the valve seat <NUM> in a direction perpendicular to the axial center C3 of the valve seat <NUM>. The three openings 79a are spaced away from one another at an angle of <NUM> degrees in a circumferential direction of the valve seat <NUM>. The openings 79a in the valve seat <NUM> are coincide in circumferential position with and communicate with the flow paths <NUM>, <NUM>, and <NUM>, respectively. The valve seat <NUM> functions as a sealing member that seals a gap between the inner peripheral surfaces of the accommodation holes 71a and 72a and an outer peripheral surface of the valve body <NUM> to inhibit leakage of the refrigerant through the gap.

As illustrated in <FIG>, the fourth plate <NUM> includes flow paths <NUM> and <NUM> respectively communicating with the flow paths <NUM> and <NUM> in the first plate <NUM> and second plate <NUM>.

The fifth plate <NUM> is located below the fourth plate <NUM> so as to close the flow paths <NUM> and <NUM> from below.

The second control valve <NUM> switches, in accordance with an amount of rotation of the valve body <NUM>, a flow direction of the refrigerant to one of a state in which the flow path <NUM> and the flow path <NUM>, which face each other at an angle of <NUM> degrees, communicate with each other as illustrated in <FIG>, a state in which the flow path <NUM> and the flow path <NUM>, which are spaced away from each other at an angle of <NUM> degrees, communicate with each other as illustrated in <FIG>, and a state in which the flow path <NUM> and the flow path <NUM>, which are spaced away from each other at an angle of <NUM> degrees, communicate with each other as illustrated in <FIG>.

<FIG> is a plan view of a first control valve.

A first control valve <NUM> is a flow rate adjustment valve. The first control valve <NUM> changes a flow of the refrigerant at two flow paths <NUM> and <NUM> defined in the first plate <NUM>. The first control valve <NUM> includes a valve body <NUM> and a driver <NUM>. The driver <NUM> is equal in configuration to the driver <NUM> described above with reference to, for example, <FIG>.

<FIG> is an exploded perspective view of a part of the first control valve. <FIG> is a sectional view illustrating the first control valve and a refrigerant flow path around the first control valve.

The valve body <NUM> of the first control valve <NUM> is equal in configuration to the valve bodies <NUM> of the first control valves <NUM>, <NUM>, and <NUM> described above with reference to, for example, <FIG>. The valve body <NUM> of the first control valve <NUM> changes a flow of the refrigerant in the manner described above with reference to <FIG>. The valve body <NUM> has a cylindrical shape and has an opening 88a passing through the valve body <NUM> in a direction perpendicular to an axial center C4 of the valve body <NUM>. The valve body <NUM> has a height in the first direction Z, and this height is substantially equal to the sum of the thickness of the first plate <NUM> and the thickness of the second plate <NUM>.

The valve body <NUM> is accommodated in an accommodation hole (first accommodation space) 71b bored in the first plate <NUM> and an accommodation hole (second accommodation space) 72b bored in the second plate <NUM> so as to extend over the accommodation hole 71b and the accommodation hole 72b. The axial center C4 of the valve body <NUM> extends in parallel with the first direction Z which is the normal direction of the first plate <NUM>. The axial center C4 of the valve body <NUM> is aligned with centers of the accommodation holes 71b and 72b.

The first plate <NUM> and the second plate <NUM> are provided with a valve seat <NUM> that is in contact with the valve body <NUM>. The valve seat <NUM> is equal in configuration to the valve seats <NUM> of the first control valves <NUM>, <NUM>, and <NUM> described above with reference to, for example, <FIG>. The valve seat <NUM> has a cylindrical shape and has a pair of openings 89a passing through the valve seat <NUM> in a direction perpendicular to an axial center C4 of the valve seat <NUM>. The valve seat <NUM> is fitted into and fixed to the two accommodation holes 71b and 72b in each of the first plate <NUM> and the second plate <NUM>.

The first plate <NUM> and the second plate <NUM> each have the flow paths <NUM> and <NUM> respectively communicating with the accommodation holes 71b and 72b. The fourth plate <NUM> has flow paths <NUM> and <NUM> communicating with the flow paths <NUM> and <NUM>. The first control valve <NUM> is configured to adjust a flow rate of the refrigerant flowing through the flow paths <NUM>, <NUM>, <NUM>, and <NUM>.

<FIG> is an exploded perspective view of a part of a first control valve according to another example. <FIG> is a sectional view illustrating the first control valve according to the another example and a refrigerant flow path around the first control valve.

The first control valve <NUM> is a flow rate control valve, which is similar to the first control valve <NUM>. The first control valve <NUM> includes a valve body <NUM> and a driver <NUM>. The driver <NUM> is equal in configuration to the driver <NUM> described above with reference to, for example, <FIG>.

The valve body <NUM> of the first control valve <NUM> is equal in configuration to the valve bodies <NUM> of the first control valves <NUM>, <NUM>, and <NUM> described above with reference to, for example, <FIG>. The valve body <NUM> of the first control valve <NUM> changes a flow of the refrigerant in the manner described above with reference to <FIG>. The valve body <NUM> has a cylindrical shape and has an opening 91a passing through the valve body <NUM> in a direction perpendicular to an axial center C4 of the valve body <NUM>. The valve body <NUM> has a height in the first direction Z, and this height is substantially equal to a thickness of a first plate <NUM> in the first direction Z. Therefore, the height of the valve body <NUM> is lower than the height of the valve body <NUM> of the first control valve <NUM> illustrated in <FIG>.

The valve body <NUM> is accommodated in an accommodation hole (first accommodation space) 71c bored in the first plate <NUM>. The axial center C5 of the valve body <NUM> extends in parallel with the first direction Z which is the normal direction of the first plate <NUM>. The axial center C5 of the valve body <NUM> is aligned with a center of the accommodation hole 71c.

The first plate <NUM> is provided with a valve seat <NUM> that is in contact with the valve body <NUM>. The valve seat <NUM> is equal in configuration to the valve seats <NUM> of the first control valves <NUM>, <NUM>, and <NUM> described above with reference to, for example, <FIG>. The valve seat <NUM> has a pair of openings 92a. The valve seat <NUM> is fitted into and fixed to the accommodation hole 71c bored in the first plate <NUM>.

The first plate <NUM> has flow paths <NUM> and <NUM> communicating with the accommodation hole 71c. The second plate <NUM> has flow paths <NUM> and <NUM> communicating with the flow paths <NUM> and <NUM>. The first control valve <NUM> is configured to adjust a flow rate of the refrigerant flowing through the flow paths <NUM>, <NUM>, <NUM>, and <NUM>.

<FIG> are sectional views respectively illustrating modifications of the first control valve according to the second embodiment.

As illustrated in <FIG>, a first control valve <NUM> includes a valve body <NUM> having a conical shape, more specifically a truncated cone shape. Likewise, a first plate <NUM> has an accommodation hole 71c having a truncated cone shape. A valve seat <NUM> fitted in the accommodation hole 71c also has a truncated cone shape.

As illustrated in <FIG>, a valve body <NUM> has a conical shape, more specifically a truncated cone shape. On the other hand, an accommodation hole 71c has a cylindrical shape. A valve seat <NUM> fitted into an accommodation hole 71c has a cylindrical outer peripheral surface and a conical (truncated cone-shaped) inner peripheral surface.

According to the modifications illustrated in <FIG>, the valve body <NUM> is externally inserted into the accommodation hole 71c in the first plate <NUM> with ease. Therefore, the refrigerant pipe unit <NUM> is manufactured with ease. The conical valve body is also applicable to each of the control valves <NUM>, <NUM>, <NUM>, and <NUM> described above in the first embodiment and each of the control valves <NUM> and <NUM> described above in the second embodiment.

In addition, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> of the control valve changes the flow of the refrigerant at the refrigerant flow path, in accordance with the amount of rotation. Therefore, for example, an inlet-side refrigerant flow path through which the refrigerant flows into the refrigerant passage 43a, 44a, 77a, 88a, 91a in the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> and an outlet-side refrigerant flow path through which the refrigerant flows out of the refrigerant passage 43a, 44a, 77a, 88a, 91a can be arranged in a linear or planar form in a direction crossing the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>. This configuration therefore reduces a space for the refrigerant flow paths in the direction of the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>, and achieves a reduction in size of the refrigerant pipe unit <NUM>, <NUM>.

In each of the foregoing embodiments, the refrigerant passage 43a, 44a, 77a, 88a, 91a defined in the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> extends in a direction perpendicular to the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>. Specifically, the entire refrigerant passage 43a, 44a, 77a, 88a, 91a defined in the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> extends in the direction perpendicular to the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>. Therefore, the inlet-side refrigerant flow path and the outlet-side refrigerant flow path are arranged in the direction perpendicular to the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>.

In each of the foregoing embodiments, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> has the axial center of rotation C1, C2, C3, C4, C5 extending in parallel with a normal direction of the first plate <NUM>, <NUM>. This configuration therefore achieves a reduction in size of the refrigerant pipe unit <NUM>, <NUM> in the normal direction of the first plate <NUM>, <NUM>.

Specifically, the inlet-side refrigerant flow path through which the refrigerant flows into the refrigerant passage 43a, 44a, 77a, 88a, 91a in the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> and the outlet-side refrigerant flow path through which the refrigerant flows out of the refrigerant passage 43a, 44a, 77a, 88a, 91a in the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> are arranged in the linear or planar form in the direction crossing the axial center of rotation C1, C2, C3, C4, C5 of the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> (i.e., the direction along the surface of the first plate <NUM>, <NUM>). This configuration therefore achieves a reduction in size of the refrigerant pipe unit <NUM> in the normal direction of the first plate <NUM>, <NUM>.

(<NUM>) In each of the foregoing embodiments, the first plate <NUM>, <NUM> includes a first accommodation space <NUM>, 51j, 71a, 71b, 71c communicating with the refrigerant flow path, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> is accommodated in the first accommodation space <NUM>, 51j, 71a, 71b, 71c, and the first plate <NUM>, <NUM> is provided with a valve seat (a first valve seat) <NUM>, <NUM>, <NUM>, <NUM>, <NUM> that is in contact with the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> in the first accommodation space <NUM>, 51j, 71a, 71b, 71c. Therefore, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> can be directly disposed in the first plate <NUM>, <NUM>, and the control valve can be constituted of the valve seat <NUM>, <NUM>, <NUM>, <NUM>, <NUM> disposed in the first plate <NUM>, <NUM>, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>, and the driver <NUM>, <NUM>. This configuration also achieves a reduction in size of the refrigerant pipe unit <NUM>, <NUM>.

(<NUM>) In each of the foregoing embodiments, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> has a cylindrical shape or a conical shape. Therefore, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> can be easily inserted into and accommodated in the first accommodation space <NUM>, 51j, 71a, 71b, 71c from the outside of the first plate <NUM>, <NUM> along the axial center C1, C2, C3, C4, C5.

(<NUM>) In each of the foregoing embodiments, the valve seat <NUM>, <NUM>, <NUM>, <NUM>, <NUM> includes a sealing member disposed in the first plate <NUM>, <NUM>. This configuration therefore ensures hermeticity between the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> and the valve seat <NUM>, <NUM>, <NUM>, <NUM>, <NUM> corresponding to the sealing member and inhibits leakage of the refrigerant.

(<NUM>) In the second embodiment, the second plate <NUM> includes a second accommodation space 72a, 72b communicating with the refrigerant flow path, and the valve body <NUM>, <NUM> is accommodated in the first accommodation space 71a, 71b and the second accommodation space 72a, 72b so as to extend over the first accommodation space 71a, 71b and the second accommodation space 72a, 72b. The second plate <NUM> is provided with a valve seat (a second valve seat) <NUM>, <NUM> that is in contact with the valve body <NUM>, <NUM> in the second accommodation space 72a, 72b. As described above, the valve body <NUM>, <NUM> is disposed on the two plates <NUM> and <NUM> so as to extend over the two plates <NUM> and <NUM>, which leads to an increase in flow rate of the refrigerant through the control valve. In the second embodiment, the first valve seat <NUM>, <NUM> disposed in the first accommodation space 71a, 71b is integrated with the second valve seat <NUM>, <NUM> disposed in the second accommodation space 72a, 72b. The first valve seat <NUM>, <NUM> may alternatively be provided separately from the second valve seat <NUM>, <NUM>.

(<NUM>) In each of the foregoing embodiments, the refrigerant pipe unit further includes a third plate <NUM>, <NUM> that is stacked on the first plate <NUM>, <NUM>, is disposed opposite the second plate <NUM>, <NUM> across the first plate <NUM>, <NUM> in a normal direction of the first plate <NUM>, <NUM>, and covers the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM>, a brazing portion joining the first plate <NUM>, <NUM> and the second plate <NUM>, <NUM> together, and a welding portion joining the first plate <NUM>, <NUM> and the third plate <NUM>, <NUM> together. Therefore, the first plate <NUM>, <NUM> and the second plate <NUM>, <NUM>, which are the constituent elements of the unit main body <NUM>, <NUM> other than the third plate <NUM>, <NUM>, can be integrated with each other by brazing. Thereafter, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> of the control valve can be accommodated in one of or both the first plate <NUM>, <NUM> and the second plate <NUM>, <NUM>. The third plate <NUM>, <NUM> can be mounted to the first plate <NUM>, <NUM>. The valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> can be covered with the third plate <NUM>, <NUM>. Hence, the valve body <NUM>, <NUM>, <NUM>, <NUM>, <NUM> and the valve seat <NUM>, <NUM>, <NUM>, <NUM>, <NUM> can be less susceptible to a thermal influence in joining the first plate <NUM>, <NUM> and the second plate <NUM>, <NUM> by brazing.

(<NUM>) In each of the foregoing embodiments, the refrigerant pipe unit <NUM>, <NUM> further includes a first control valve <NUM>, <NUM>, <NUM>, <NUM>, <NUM> configured to adjust the flow rate of the refrigerant in accordance with the amount of rotation of the valve body <NUM>, <NUM>, <NUM>, and a second control valve <NUM>, <NUM> configured to switch the flow direction of the refrigerant in accordance with the amount of rotation of the valve body <NUM>, <NUM>. This configuration allows the refrigerant pipe unit <NUM>, <NUM> to have a function of controlling multiple flows of the refrigerant. For example, the accommodation space accommodating the valve body is not limited to the accommodation hole passing through one of or both the first plate and the second plate. The accommodation space accommodating the valve body may alternatively be an accommodation recess to be formed by recessing the surface of one of the first plate and the second plate or recessing surfaces of both the first plate and the second plate.

The refrigerant passage in the valve body is not limited to the hole passing through the valve body. The refrigerant passage may alternatively be a recessed groove to be formed in the outer peripheral surface of the valve body. The valve body of the control valve may be accommodated in only the second plate. The valve body may be disposed in the refrigerant pipe unit with the axial center oriented toward a direction crossing the first direction.

In each of the foregoing embodiments, the valve seat is configured with the sealing member provided separately from one of or both the first plate and the second plate. However, the sealing member is omittable. For example, the valve body is brought into direct contact with the inner peripheral surface of the accommodation hole in one of the first plate and the second plate or the inner peripheral surfaces of the accommodation holes in both the first plate and the second plate. The inner peripheral portion of the accommodation hole can thus be used as the valve seat.

In the foregoing embodiments, the hole, through which the another refrigerant pipe is connected to the flow path in the unit main body, is bored in the upper surface of the unit main body (i.e., the upper surface of the first or third plate). The hole may alternatively be bored in a lower surface or a side surface of the unit main body.

The valve body may have, for example, a spherical shape in addition to the cylindrical shape or the conical shape.

Claim 1:
A refrigerant pipe unit comprising:
a first plate (<NUM>, <NUM>);
a second plate (<NUM>, <NUM>) stacked on the first plate (<NUM>, <NUM>); and
a control valve (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>, <NUM>, <NUM>),
wherein
one of or both the first plate (<NUM>, <NUM>) and the second plate (<NUM>, <NUM>) includes or include a refrigerant flow path, and
the control valve (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>, <NUM>, <NUM>) includes:
a valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>) including a refrigerant passage (43a, 44a, 77a, 88a, 91a) communicating with the refrigerant flow path,
the valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>) rotatably disposed in the first plate (<NUM>, <NUM>),
the valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>) configured to change a flow of a refrigerant at the refrigerant flow path, in accordance with an amount of rotation; and
a driver (<NUM>, <NUM>) configured to adjust the amount of rotation of the valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>);
wherein the valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>) has an axial center of rotation (C1, C2, C3, C4, C5) extending in parallel with a normal direction (Z) of the first plate (<NUM>, <NUM>); and
characterized in that the refrigerant passage (43a, 44a, 77a, 88a, 91a) extends in a direction perpendicular to an axial center of rotation (C1, C2, C3, C4, C5) of the valve body (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>), so that an inlet-side refrigerant flow path through which the refrigerant flows into the refrigerant passage in the valve body and an outlet-side refrigerant flow path through which the refrigerant flows out of the refrigerant passage in the valve body is arranged in a linear or planar form in a direction crossing the axial center of rotation of the valve body.