JP2006220156A - Steam compression type refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce mechanical loss of a radial type fluid machine such as an expander. <P>SOLUTION: A sliding axial line CLp of a plunger is deviated from the center of rotation of a rotary cylinder 12. Consequently, when refrigerant flowing into an operation chamber 12b makes force in the direction for enlarging volume of the operation chamber 12b act on the plunger 13, reaction force F that the plunger 13 receives from an internal wall 11a of a rotary liner 11 can be used as force for rotating the rotary cylinder 12 as it is. Since the direction of sliding axial line CLp of the plunger of the reaction force F agrees with the direction of reaction force F, force for increasing friction resistance of the plunger 13 and an internal wall of an insertion hole 12a is not generated easily, thereby reducing mechanical loss. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a radial fluid machine, and is effective when applied to an expander that recovers mechanical energy while decompressing and expanding a high-pressure fluid, or a compressor or pump that sucks and discharges fluid.

  For example, Japanese Patent Application Laid-Open No. 10-19401 is known as an invention that uses an expander to reduce power consumption of a vapor compression refrigerator.

  By the way, the expander recovers mechanical energy from the high-pressure fluid by expanding the high-pressure fluid in an isentropic manner. As is apparent from the Mollier diagram shown in FIG. Since the slope of the isentropic line increases and the amount of change in enthalpy with respect to the amount of change in pressure decreases, the maximum theoretical value of energy that can be recovered during decompression expansion is significantly smaller than the energy required during compression.

  Therefore, if the mechanical loss of the expander is large, the recovered energy is consumed due to the mechanical loss, and there is a possibility that the power consumption of the vapor compression refrigerator cannot be sufficiently reduced.

  In view of the above points, an object of the present invention is to reduce the mechanical loss of a radial fluid machine such as an expander.

  In order to achieve the above object, according to the present invention, the rotating liner (11) is provided in the rotating liner (11), and is displaced from the rotation center of the rotating liner (11). The rotary cylinder (12) that rotates with the rotation center axis parallel to the rotation center axis of the rotary liner (11) and the insertion hole (12a) formed in the rotation cylinder (12) A plunger (13) accommodated therein, and the plunger (13) is a rotating liner (11) according to a change in volume of an operation chamber (12b) constituted by the insertion hole (12a) and the plunger (13) A plunger sliding axis (C) parallel to the sliding direction of the plunger (13) through the center of the cross section of the plunger (13) is received from the inner wall side of the working chamber (12b). p) is characterized in that is offset from the rotational center of the rotary cylinder (12).

  As a result, the force that the plunger (13) receives as a reaction force from the rotary liner (11) can directly become the force that rotates the rotary cylinder (12), so the frictional resistance between the plunger (13) and the inner wall of the insertion hole (12a). It is difficult to generate a force that increases

  In the invention described in claim 2, the rotating liner (11) that rotates, and the rotation center of the rotating liner (11) provided in the rotating liner (11) and at a position deviated from the rotation center of the rotating liner (11). A rotating cylinder (12) that rotates with a rotation center axis parallel to the axis, and a plunger (13) that is slidably received in an insertion hole (12a) formed in the rotating cylinder (12). The plunger (13) increases the volume of the working chamber (12b) from the inner wall side of the rotary liner (11) according to the volume change of the working chamber (12b) constituted by the insertion hole (12a) and the plunger (13). When the force (F) applied to the plunger (13) by the rotating liner (11) is substantially maximized, the direction of the force (F) is the sliding direction of the plunger (13). When Characterized by comprising parallel.

  As a result, the force that the plunger (13) receives as the reaction force of the rotating liner (11) can directly become the force that rotates the rotating cylinder (12), so that the frictional resistance between the plunger (13) and the inner wall of the insertion hole (12a) is reduced. Less force to increase.

  In the invention described in claim 3, the rotating liner (11) that rotates, and the rotation center of the rotating liner (11) provided in the rotating liner (11) and at a position deviated from the rotation center of the rotating liner (11). A rotating cylinder (12) that rotates with a rotation center axis parallel to the axis, and a plunger (13) that is slidably received in an insertion hole (12a) formed in the rotating cylinder (12). The plunger (13) increases the volume of the working chamber (12b) from the inner wall side of the rotary liner (11) according to the volume change of the working chamber (12b) constituted by the insertion hole (12a) and the plunger (13). When the force (F) exerted on the plunger (13) by the rotating liner (11) is substantially maximized, the plunger (1) passes through the center of the cross section of the plunger (13). Sliding direction parallel to the plunger sliding axis of) (CLp) is characterized by passing through the rotation center of the rotating liner (11).

  As a result, the force that the plunger (13) receives as the reaction force of the rotating liner (11) can directly become the force that rotates the rotating cylinder (12), so that the frictional resistance between the plunger (13) and the inner wall of the insertion hole (12a) is reduced. Less force to increase.

  In invention of Claim 4, the plunger front-end | tip part (13a) which receives the force (F) from a rotation liner (11) among the plungers (13) is formed in the curved surface shape, and also in plunger (13) The portion (11a) that contacts and applies the force (F) from the rotating liner (11) to the plunger (13) is formed in a curved surface having a radius of curvature larger than the radius of curvature of the plunger tip (13a). It is characterized by that.

  Thereby, it can suppress that the contact surface pressure in the front end side (13a) of the plunger 1 (13) increases.

  The invention according to claim 5 is characterized in that the plunger tip (13a) is in direct contact with the inner wall (11a) of the rotary liner (11).

  Thereby, the number of parts can be reduced as compared with a conventional radial type fluid machine shown in FIG.

  In the sixth aspect of the invention, the substantially cylindrical valve means (14) for opening and closing the intake / exhaust port (18) for communicating the working chamber (12b) with the outside is disposed at the rotation center of the rotary cylinder (12). Furthermore, the port axis (CL) passing through the cross-sectional center of the intake / exhaust port (18) passes through the cross-sectional center of the plunger (13), and the axis (CLp) is parallel to the sliding direction of the plunger (13). It is located in the rotation center side of (12).

  Accordingly, the intake / exhaust port (18) can be communicated at a smaller intake / exhaust angle than that in which the port axis (CL) coincides with the axis (CLp).

  The suction / discharge angle refers to a circumferential angle required for the entire cross-sectional area of the suction / discharge port (18) to communicate with the valve means (14), as shown in FIG.

  In the invention according to claim 7, the valve means (14) changes the opening / closing timing of the intake / exhaust port (18) with respect to the rotation angle of the rotating cylinder (12) by displacing the valve means (14) in the longitudinal direction. It is comprised so that it can be performed.

  Thereby, as will be described later, the vapor compression refrigerator can be operated efficiently.

  In the invention according to claim 8, the compressor (1) for sucking and compressing the refrigerant, the radiator (3) for cooling the refrigerant discharged from the compressor (1), and the refrigerant flowing out from the radiator (3) The radial fluid machine (4) according to claim 7 and the evaporation that evaporates the refrigerant expanded under reduced pressure, wherein mechanical energy is recovered while decompressing and expanding, and the recovered mechanical energy is given to the compressor (1). And an actuator (19a, 20, 21) for displacing the valve means (14) in the longitudinal direction using the refrigerant pressure.

  Thereby, for example, the vapor compression refrigerator can be operated efficiently.

  In the invention according to claim 9, the compressor (1) for sucking and compressing the refrigerant, the radiator (3) for cooling the refrigerant discharged from the compressor (1), and the refrigerant flowing out from the radiator (3) The radial type fluid machine (4) according to any one of claims 1 to 7, wherein the mechanical energy is recovered while decompressing and expanding, and the recovered mechanical energy is supplied to the compressor (1), And an evaporator (5) for evaporating the generated refrigerant.

  Thereby, as will be described later, the vapor compression refrigerator can be operated efficiently.

  As in the invention described in claim 10, the refrigerant pressure in the radiator (3) may be equal to or higher than the critical pressure of the refrigerant.

  Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.

(First embodiment)
In this embodiment, the radial fluid machine according to the present invention is applied to an expander of a vapor compression refrigerator, and FIG. 1 is a schematic diagram of the vapor compression refrigerator, and FIGS. 4 is an axial sectional view of the machine, FIG. 4 is an AA sectional view of FIG. 2, FIG. 5 is an enlarged view showing a connection portion between the valve 14 and the intake / exhaust port 18, and FIG. FIG. 6B is a cross-sectional view taken along the line II of the valve 14, and FIG. 6C is a cross-sectional view taken along the line II-II of the valve 14.

  First, the configuration of the vapor compression refrigerator will be described with reference to FIG.

  The compressor 1 obtains power from the electric motor 2 and sucks and compresses the refrigerant, and the radiator 3 is a high-pressure side heat exchanger that cools the refrigerant discharged from the compressor 1. The expander 4 recovers mechanical energy while decompressing and expanding the high-pressure refrigerant flowing out of the radiator 3, and gives the recovered mechanical energy to the motor 2 to indirectly supply the recovered energy to the compressor 1. The evaporator 5 is a low-pressure side heat exchanger that evaporates the refrigerant expanded under reduced pressure.

  In this embodiment, carbon dioxide is used as the refrigerant, and when the heat load on the evaporator 5 or the radiator 3 side is large, the refrigerant pressure in the radiator 3, that is, the discharge pressure of the compressor 1 is set to the refrigerant. Raised above the critical pressure to obtain the necessary capacity.

  Incidentally, in the present embodiment, the compressor 1, the motor 2, and the expander 4 are integrated by connecting their shafts in series to form an expander-integrated compressor.

  Next, the structure of the expander 4 will be described with reference to FIGS.

  As shown in FIG. 2, the expander 4 roughly includes a housing 10, a rotating liner 11, a rotating cylinder 12, a plunger 13, a valve 14, and the like.

  The rotating liner 11 has a cylindrical shape that is rotatably supported by the first cage 16 via a bearing 15a. The rotating cylinder 12 is arranged in the rotating liner 11 as shown in FIG. 11 has a substantially cylindrical shape that rotates with a rotation center axis parallel to the rotation center axis of the rotary liner 11 at a position shifted from the rotation center of the rotation liner 11.

  2 and 3, the rotary cylinder 12 is supported by the first cage 16 and the second cage 17 through bearings 15b and 15c, and the motor 2 is mounted on the rotary shaft 12c. The first and second cages 16 and 17 are press-fitted and fixed in the housing 10.

  As shown in FIG. 4, the plunger 13 is a columnar piston slidably accommodated in an insertion hole 12 a formed in the rotary cylinder 12, and one end side 13 a is a curvature of the inner wall 11 a of the rotary liner 11. It is formed in a curved surface shape having a smaller radius of curvature than the radius and is in contact with the inner wall 11 a of the rotary liner 11.

  At this time, a plurality of insertion holes 12a are formed in the rotating cylinder 12 so that the plunger sliding axis CLp passing through the center of the section of the plunger 13 and parallel to the sliding direction of the plunger 13 is displaced from the rotation center of the rotating cylinder 12. In the embodiment, four are formed.

  The valve 14 is a substantially cylindrical valve means that opens and closes an intake / exhaust port 18 that is located at the rotation center of the rotary cylinder 12 and that communicates the outside, that is, the refrigerant outlet side of the radiator 3 and the working chamber 12 b. As shown in FIG. 6, a suction groove portion 14 a and a discharge groove portion 14 b that control the opening / closing timing of the suction / discharge port 18 with respect to the rotation angle of the rotary cylinder 12 are formed on the outer peripheral surface of the rotary cylinder 12. An introduction passage 14c that guides the high-pressure refrigerant that has flowed out into the working chamber 12b is formed.

  The suction groove portion 14a controls the opening / closing timing of the suction / exhaust port 18 when flowing into the working chamber 12b, and the discharge groove portion 14b controls the opening / closing timing of the suction / discharge port 18 when flowing out of the working chamber 12b. is there.

  Further, as shown in FIG. 2, the valve 14 is held by the rotary cylinder 12 and the third cage 19 so as to be slidable in the longitudinal direction thereof while being prevented from rotating around the central axis by the key 14d. Has been.

  And this valve 14 is on the opposite side to the control pressure chamber 19a across the flange portion 14e and the pressure in the control pressure chamber 19a formed by the flange portion 14e formed in the valve 14 and the third cage 19. It displaces so that it stops at the position where the elastic force of the coil spring 20 as the arranged elastic means is balanced. Therefore, the valve 14 can be slid and displaced by controlling the pressure in the control pressure chamber 19a.

  Further, as shown in FIG. 5, the intake / exhaust port 18 has a plunger sliding axis CLp so that the port axis CL passing through the center of the cross section of the intake / exhaust port 18 is located closer to the rotation center of the rotary cylinder 12 than the plunger sliding axis CLp. In contrast, they are offset. Incidentally, in this embodiment, the port axis CL coincides with a cylinder radial axis (not shown) extending in the radial direction of the rotary cylinder 12 through the rotation center of the rotary cylinder 12.

  Here, the working chamber 12b is a space formed by the other end of the plunger 13 and the insertion hole 12a. In this embodiment, the refrigerant is decompressed and expanded by expanding the volume of the working chamber 12b.

  In FIG. 2, the pressure control valve 21 is a pressure control means that regulates the high-pressure refrigerant flowing out of the radiator 3 and supplies the regulated refrigerant pressure to the control pressure chamber 19a. In this embodiment, an actuator that slides and displaces the valve 14 is constituted by the control pressure chamber 19a, the coil spring 20, and the pressure control valve 21.

  Incidentally, the control pressure chamber 19a and the pressure control valve 21 are connected by a communication passage 21a, and the expander 4 and the motor 2 side are sealed by a lip seal 22.

  Next, a characteristic operation of the expander 4 according to this embodiment, that is, a radial fluid machine will be described (see FIG. 4).

  The basic operation of the radial type fluid machine is the same as that of the known radial type fluid machine, and here, the expander 4 according to the present embodiment, that is, focusing on the differences from the known radial type fluid machine, that is, The characteristic operation of the radial fluid machine will be described.

  Incidentally, as a book describing a radial type fluid machine, there is, for example, “the theory and practice of a piston pump / motor” (Ohm).

  The high-pressure refrigerant guided from the radiator 3 to the valve 14 flows into the working chamber 12b connected to the intake / exhaust port 18 communicating with the suction groove 14a. The refrigerant that has flowed into the working chamber 12b causes the plunger 13 to act on the plunger 13 in a direction that expands the volume of the working chamber 12b. Therefore, the distal end side 13a of the plunger 13 is oriented to increase the inner diameter of the rotary liner 11. Is applied to the inner wall 11 a of the rotary liner 11.

  At this time, the plunger 13 receives a force in the direction of reducing the volume of the working chamber 12b as a reaction force F from the inner wall 11a of the rotary liner 11, but the plunger slide axis CLp is displaced from the rotation center of the rotary cylinder 12. Therefore, the reaction force F from the inner wall 11 a of the rotary liner 11 becomes a force for rotating the rotary cylinder 12.

  The refrigerant flowing into the working chamber 12b expands the working chamber 12b by pressing the plunger 13 against the inner wall 11a side of the rotary liner 11, and expands under reduced pressure.

  In FIG. 4, the working chamber 12b at the position shown in (1) shows a state immediately after the suction of the refrigerant is completed, and is the time when the reaction force F becomes the largest. The working chamber 12b at the position shown in (2) shows the end of the expansion process, the working chamber 12b at the position shown in (3) shows a discharge process for discharging the refrigerant after the expansion, and (4) The working chamber 12b at the indicated position shows a state immediately before starting the suction of the refrigerant.

  Further, when the valve 14 is displaced in the axial direction, the suction / discharge angle θ (see FIG. 5) of the valve 14 in which the suction groove portion 14a and the discharge groove portion 14b communicate with the suction / discharge port 18 with respect to the rotation angle of the rotary cylinder 12 changes. Since the shapes of the suction groove portion 14a and the discharge groove portion 14b are selected as described above, the amount of refrigerant introduced into the working chamber 12b is variably controlled by controlling the pressure in the control pressure chamber 19a by the pressure control valve 21. Can do.

  Next, the function and effect of this embodiment will be described.

  FIG. 7 is a cross-sectional view showing the characteristics of a known radial type fluid machine. In this embodiment, the plunger slide axis CLp is deviated from the rotation center of the rotary cylinder 12, whereas in the known radial type fluid machine, The plunger slide axis CLp is aligned with the rotation center of the rotary cylinder 12.

  Here, when the reaction force F becomes substantially maximum, that is, when the present embodiment is compared with a known radial type fluid machine at the position shown in FIG. 4 and (1), the inner wall 11a of the rotary liner 11 is a plunger. In the known radial type fluid machine, the direction of the reaction force F acting on the direction 13 is the direction from the contact point between the plunger 13 and the inner wall 11a toward the rotation center of the rotary liner 11, and the known radial type fluid machine. Since the direction of the reaction force F plunger slide axis CLp and the direction of the reaction force F are different, the reaction force F does not directly become a force for rotating the rotary cylinder 12.

  That is, in the known radial type fluid machine, when the reaction force F becomes substantially maximum, the force Fr of the direction component perpendicular to the plunger sliding axis CLp becomes the force that rotates the rotary cylinder 12. At this time, the force Fr becomes a factor that increases the frictional resistance between the plunger 13 and the inner wall of the insertion hole 12a.

  On the other hand, in the present embodiment, the reaction force F becomes the force that rotates the rotary cylinder 12 as it is, and the direction of the reaction force F plunger sliding axis CLp and the direction of the reaction force F coincide with each other. A force that increases the frictional resistance between the plunger 13 and the inner wall of the insertion hole 12a hardly occurs.

  Therefore, according to the expander 4 which concerns on this embodiment, ie, a radial type fluid machine, mechanical loss can be reduced compared with a known radial type fluid machine.

  Further, since the port axis CL is located closer to the rotation center of the rotary cylinder 12 than the plunger sliding axis CLp, the port axis CL is smaller than the case where the port axis CL coincides with the plunger sliding axis CLp. The suction / discharge port 18 and the suction groove 14a or the discharge groove 14b can be communicated with each other.

  Therefore, the error of the suction / discharge angle θ due to the manufacturing variation of the valve 14 and the operation variation of the valve 14, that is, the difference between the control target suction / discharge amount and the actual suction / discharge amount can be reduced.

  Further, in the present embodiment, the distal end side 13a of the plunger 13 is in contact with a curved surface larger than the curvature radius of the curved surface formed on the distal end side 13a, that is, the inner wall 11a of the rotary liner 11, whereas FIG. In the illustrated radial fluid machine, a slipper 100 is interposed between the plunger 13 and the inner wall 11a.

  Therefore, in this embodiment, it is possible to suppress an increase in the contact surface pressure on the distal end side 13a of the plunger 13 while reducing the number of parts as compared with the radial type fluid machine shown in FIG.

  Moreover, since the density of the refrigerant flowing into the expander 4 changes when the heat load in the radiator 3 or the evaporator 5 changes, it is desirable to change the amount of refrigerant flowing into the expander 4 according to the heat load.

  On the other hand, in the present embodiment, as described above, the amount of refrigerant flowing into the expander 4 can be easily controlled, so that the vapor compression refrigerator can be operated efficiently.

  2 shows a state where the amount of refrigerant flowing into the expander 4 is minimized, and FIG. 3 shows a state where the amount of refrigerant flowing into the expander 4 is minimized.

(Second Embodiment)
In the first embodiment, the radial fluid machine according to the present invention is applied to an expander. However, in the present embodiment, the radial fluid machine according to the present invention is applied to a compressor or a pump.

  FIG. 8 is a sectional view in the axial direction of the radial fluid machine according to the present embodiment. The largest difference between the first embodiment in which the present invention is applied as an expander and the present embodiment in which the present invention is applied to a compressor or a pump. The point is that the fluid flow and the direction of rotation of the rotating cylinder 12 and the rotating liner 11 are reversed, and the other basic operations and features are the same.

  In FIG. 8, the discharge valve 14 f is a reed valve-like valve that prevents the discharged fluid from flowing backward, and the stopper 14 g regulates the maximum opening of the discharge valve 14.

(Other embodiments)
In the above-described embodiment, the direction of the reaction force F coincides with the plunger sliding axis CLp when the reaction force F becomes substantially maximum. In other words, the plunger sliding axis CLp when the reaction force F becomes substantially maximum. However, the present invention is not limited to this, and the reaction force F is approximately the maximum when the reaction force F is substantially maximum. The direction of F may be different from the plunger sliding axis CLp.

  In the above-described embodiment, the port axis CL coincides with the cylinder radial axis, but the present invention is not limited to this.

  In the above-described embodiment, the curved surface of the inner wall 11a of the rotary liner 11 is used as it is, and the curvature radius of the curved surface that contacts the distal end side 13a of the plunger 13 is made larger than the curvature radius of the distal end side 13a. Instead, as shown in FIG. 9, a recess 11b having a curved surface having a radius of curvature larger than the radius of curvature of the distal end side 13a may be formed.

  Further, in the above-described embodiment, the actuator that regulates the refrigerant pressure by the control pressure chamber 19a, the coil spring 20, and the pressure control valve 21 and slides and displaces the valve 14 is configured. However, the present invention is limited to this. However, an actuator using electromagnetic force such as a motor or an actuator using a piezoelectric element may be used.

  In the above-described embodiment, the expander 4, the motor 2, and the compressor 1 are integrated in series in the order, but the present invention is not limited to this, and for example, as shown in FIG. In addition, the expander 4 may be connected in series to the compressor 1 of the electric compressor.

  In the above embodiment, the radial fluid machine according to the present invention is applied to the vapor compression refrigerator, but the application of the present invention is not limited to this.

  In the above-described embodiment, in the vapor compression refrigerator, carbon dioxide is used as a refrigerant, and the refrigerant pressure on the high pressure side is set to be equal to or higher than the critical pressure of the refrigerant. However, the present invention is not limited to this.

  In the above-described embodiment, the rotary liner 11 is cylindrical and the rotary cylinder 12 is columnar. However, the present invention is not limited to this, and the tip 13a of the plunger 13 is the inner wall 11a of the rotary liner 11. For example, the inner wall of the rotary liner 11 and the outer periphery of the rotary cylinder 12 may be polygonal.

  Further, in this specification, “the plunger sliding axis CLp passes through the center” does not mean that the center is strictly located at the plunger sliding axis CLp. This means that CLp passes through the center.

It is a mimetic diagram of a vapor compression refrigeration machine concerning an embodiment of the present invention. It is an axial sectional view of the expander concerning a 1st embodiment of the present invention. It is an axial sectional view of the expander concerning a 1st embodiment of the present invention. It is AA sectional drawing of FIG. It is an enlarged view which shows the connection part of the valve | bulb 14 and the intake / exhaust port 18 of the expander which concerns on embodiment of this invention. (A) is a perspective view of the valve 14, (b) is a sectional view taken along the line II of the valve 14, and (c) is a sectional view taken along the line II-II of the valve 14. It is an axial sectional view of a radial type fluid machine according to the prior art. It is an axial sectional view of a compressor concerning a 2nd embodiment of the present invention. It is an enlarged view of the plunger front-end | tip part of the radial type fluid machine which concerns on other embodiment of this invention. It is a schematic diagram of an expander-integrated electric compressor according to another embodiment of the present invention. It is a Mollier diagram.

Explanation of symbols

11 ... Rotating liner, 12 ... Rotating cylinder, 13 ... Plunger,
14 ... Valve, 14a ... Suction groove, 14b ... Discharge groove, 14c ... Introduction passage.

Claims (10)

A rotating liner (11) that rotates;
A rotating cylinder that is provided in the rotating liner (11) and rotates with a rotation center axis parallel to the rotation center axis of the rotating liner (11) at a position deviated from the rotation center of the rotating liner (11). (12)
A plunger (13) slidably accommodated in an insertion hole (12a) formed in the rotating cylinder (12);
The plunger (13) is moved from the inner wall side of the rotary liner (11) to the working chamber (12b) according to the volume change of the working chamber (12b) constituted by the insertion hole (12a) and the plunger (13). ) To reduce the volume,
Furthermore, the plunger slide axis (CLp) passing through the center of the cross section of the plunger (13) and parallel to the sliding direction of the plunger (13) is offset from the rotation center of the rotary cylinder (12). Radial type fluid machine. A rotating liner (11) that rotates;
A rotating cylinder that is provided in the rotating liner (11) and rotates with a rotation center axis parallel to the rotation center axis of the rotating liner (11) at a position deviated from the rotation center of the rotating liner (11). (12)
A plunger (13) slidably accommodated in an insertion hole (12a) formed in the rotating cylinder (12);
The plunger (13) is moved from the inner wall side of the rotary liner (11) to the working chamber (12b) according to the volume change of the working chamber (12b) constituted by the insertion hole (12a) and the plunger (13). ) To reduce the volume,
Further, when the force (F) applied to the plunger (13) by the rotary liner (11) is substantially maximum, the direction of the force (F) is substantially parallel to the sliding direction of the plunger (13). A radial fluid machine characterized by that. A rotating liner (11) that rotates;
A rotating cylinder that is provided in the rotating liner (11) and rotates with a rotation center axis parallel to the rotation center axis of the rotating liner (11) at a position deviated from the rotation center of the rotating liner (11). (12)
A plunger (13) slidably accommodated in an insertion hole (12a) formed in the rotating cylinder (12);
The plunger (13) is moved from the inner wall side of the rotary liner (11) to the working chamber (12b) according to the volume change of the working chamber (12b) constituted by the insertion hole (12a) and the plunger (13). ) To reduce the volume,
Further, when the force (F) applied to the plunger (13) by the rotary liner (11) is substantially maximized, it passes through the center of the section of the plunger (13) and is parallel to the sliding direction of the plunger (13). A radial fluid machine characterized in that the plunger sliding axis (CLp) passes through the rotation center of the rotary liner (11). The plunger tip (13a) that receives the force (F) from the rotary liner (11) of the plunger (13) is formed in a curved surface shape,
Further, a portion (11a) that contacts the plunger (13) and applies force (F) from the rotary liner (11) to the plunger (13) is larger than the radius of curvature of the plunger tip (13a). The radial fluid machine according to claim 1, wherein the radial fluid machine is formed in a curved shape having a radius of curvature. The radial fluid machine according to claim 4, wherein the plunger tip (13a) is in direct contact with the inner wall (11a) of the rotary liner (11). A substantially cylindrical valve means (14) for opening and closing an intake / exhaust port (18) for communicating the working chamber (12b) with the outside is disposed at the rotation center of the rotary cylinder (12),
Furthermore, the port axis (CL) passing through the center of the cross section of the intake / exhaust port (18) passes through the center of the cross section of the plunger (13), and the rotation is performed from the axis (CLp) parallel to the sliding direction of the plunger (13). The radial fluid machine according to any one of claims 1 to 5, wherein the radial fluid machine is located on a rotation center side of the cylinder (12). The valve means (14) can change the opening / closing timing of the intake / exhaust port (18) with respect to the rotation angle of the rotating cylinder (12) by displacing the valve means (14) in the longitudinal direction. The radial fluid machine according to claim 6, wherein the radial fluid machine is configured. A compressor (1) for sucking and compressing refrigerant;
A radiator (3) for cooling the refrigerant discharged from the compressor (1);
The radial fluid machine (4) according to claim 7, wherein mechanical energy is recovered while decompressing and expanding the refrigerant flowing out of the radiator (3), and the recovered mechanical energy is given to the compressor (1). When,
An evaporator (5) for evaporating the refrigerant expanded under reduced pressure;
A vapor compression refrigerator comprising an actuator (19a, 20, 21) for displacing the valve means (14) in the longitudinal direction using refrigerant pressure. A compressor (1) for sucking and compressing refrigerant;
A radiator (3) for cooling the refrigerant discharged from the compressor (1);
The mechanical energy is recovered while decompressing and expanding the refrigerant flowing out of the radiator (3), and the recovered mechanical energy is given to the compressor (1). A radial fluid machine (4);
A vapor compression refrigerator having an evaporator (5) for evaporating a refrigerant expanded under reduced pressure. The vapor compression refrigerator according to claim 8 or 9, wherein the refrigerant pressure in the radiator (3) may be equal to or higher than a critical pressure of the refrigerant.

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