JPWO2007052569A1 - Expander and heat pump using the same - Google Patents

Abstract

The expander of the present invention includes n rotary fluid mechanisms (n is an integer of 2 or more), a first suction hole 41b that sucks working fluid into the suction-side space 55a of the first fluid mechanism 41, and k A communication hole 43a connecting the discharge side space 55b of the th (k is an integer from 1 to n-1) fluidic space 55b and the (k + 1) th suction side space 56a to form one space, and the n th fluid mechanism And a discharge hole 51a for discharging the working fluid from the discharge side space. A connection position of the first fluid mechanism 41 with the suction side space 55a is variable, and a second suction hole 72f that sucks the working fluid into the suction side space 55a is further provided.

Description

  The present invention relates to an expander applied to a refrigeration cycle apparatus (heat pump), and further to a heat pump using the expander.

  There has been proposed a power recovery type refrigeration cycle in which expansion energy of a working fluid (refrigerant) is recovered by an expander, and the recovered energy is used as part of the work of the compressor. As such a refrigeration cycle, for example, a refrigeration cycle using a fluid machine in which an expander and a compressor are connected by a shaft (hereinafter referred to as an “expander-integrated compressor”) is known. (Japanese Patent Laid-Open No. 2001-116371).

  Hereinafter, a refrigeration cycle using an expander-integrated compressor will be described.

  FIG. 20 shows a refrigeration cycle using a conventional expander-integrated compressor. In this refrigeration cycle, the compressor 1, the gas cooler (heat radiator) 2, the expander 3 and the evaporator 4 constitute a main circuit 8 of working fluid (refrigerant). The compressor 1, the expander 3, and the rotary motor 6 Is connected to the shaft 7 to form an expander-integrated compressor. The refrigerant circuit includes a sub circuit 9 together with the main circuit 8. The sub circuit 9 branches from the main circuit 8 on the outlet side of the gas cooler 2, and merges with the main circuit 8 on the inlet side of the evaporator 4. The working fluid passing through the main circuit 8 is expanded in the expander 3, and the working fluid passing through the sub circuit 9 is expanded by the expansion valve 5.

  The working fluid is compressed from a low temperature and a low pressure to a high temperature and a high pressure in the compressor 1 and then cooled to a low temperature and a high pressure in the gas cooler 2. And after expanding to low temperature low pressure (gas-liquid two phases) in the expander 3 or the expansion valve 5, it is heated by the evaporator 4 and returns to low temperature low pressure (gas phase). The expander 3 collects expansion energy of the working fluid and converts it into rotational energy of the shaft 7. This rotational energy is used as a part of work for driving the compressor 1, and as a result, the power of the rotary motor 6 can be reduced.

  Here, the operation of the refrigeration cycle when the expansion valve 5 is fully closed and the mass flow rate of the working fluid in the sub circuit 9 is zero will be described.

  If the suction volume of the compressor 1 is Vcs, the suction volume of the expander 3 is Ves, and the rotational speed of the shaft 7 is N, the volume flow rate of the working fluid on the inlet side of the compressor 1 and the inlet side of the expander 3 The volume flow rates of the working fluid are (Vcs × N) and (Ves × N), respectively. Since the mass flow rate of the working fluid in the sub circuit 9 is zero, the mass flow rate in the compressor 1 and the mass flow rate in the expander 3 are equal. Assuming that this mass flow rate is G, the density of the working fluid on the inlet side of the compressor 1 and the density of the working fluid on the inlet side of the expander 3 can be calculated from the ratio of the respective volume flow rate and mass flow rate {G / ( Vcs × N)}, {G / (Ves × N)}. From these equations, the ratio of the density of the working fluid on the inlet side of the compressor 1 and the density of the working fluid on the inlet side of the expander 3 is {G / (Vcs × N)} / {G / (Ves × N )}, That is, (Ves / Vcs) and becomes constant.

FIG. 21 shows a Mollier diagram of the refrigeration cycle. In the figure, the compression process in the compressor 1 corresponds to AB, the heat release process in the gas cooler 2 corresponds to BC, the expansion process in the expander 3 corresponds to CD, and the evaporation process in the evaporator 4 corresponds to DA. Since the density ratio of the working fluid at the point A on the inlet side of the compressor 1 and the point C on the inlet side of the expander 3 is constant at (Ves / Vcs), the density of the working fluid at the point A is ρ _0. Then, the density ρ _c at the point C is (Vcs / Ves) ρ ₀ . Assuming that the density of point A is constant, when the pressure at point C is increased, it changes from point C to point C ′ on the line ρ _c = (Vcs / Ves) ρ _0. Become. That is, it becomes impossible to change the point C to the point C ″ increased by the pressure along the isotherm (T = T _c ), and the free control of the refrigeration cycle is hindered. Since there is an optimum high pressure at which the coefficient of performance (COP) is maximum at the heat source temperature (for example, Japanese Patent Application Laid-Open No. 2002-81766), efficient operation cannot be performed unless the temperature and pressure are freely controlled.

  The restriction that the ratio of the density on the inlet side of the compressor 1 and the density on the inlet side of the expander 3 is constant is that the mass flow rate in the compressor 1 and the mass flow rate in the expander 3 are equal, and the ratio of the volume flow rate. Is due to the constant. This restriction can be avoided by opening the expansion valve 5 and allowing a part of the working fluid flowing through the refrigerant circuit to flow through the sub circuit 9 (Japanese Patent Laid-Open No. 2001-116371).

  In a power recovery type heat pump using a conventional expander-integrated compressor, in order to avoid the restriction of a constant density ratio caused by the compressor and the expander having the same rotation speed, the working fluid is supplied to the expander. Along with the main circuit provided with the sub-circuit provided with the expansion valve. However, this cannot recover the expansion energy of the working fluid that passes through the subcircuit.

  The problem that the expansion energy of the working fluid cannot be efficiently recovered becomes prominent when an expander-integrated compressor is used, but also occurs when a separate expander that is not connected to the compressor by a shaft is used. . When a separation type expander is used, the expansion energy of the working fluid is recovered by a generator connected to the expander. Since the power generation efficiency of the generator decreases as it goes away from the rated speed, it is desirable that the generator be operated near the rated speed. However, in the refrigeration cycle, since the circulating amount and density of the working fluid change according to the operating conditions, it is difficult to operate the generator only near the rated speed. For this reason, even in the separation type expander, it is not easy to efficiently recover the expansion energy of the working fluid.

  This invention is made | formed in view of said situation, and it aims at providing the expander which can collect | recover the expansion energy of a working fluid efficiently. It is another object of the present invention to provide a heat pump including the expander.

That is, the present invention
A cylinder,
A shaft having an eccentric part;
A piston that fits into the eccentric part and rotates eccentrically inside the cylinder;
N rotary expansion mechanisms (n is an integer of 2 or more) having a partition member for partitioning the space between the cylinder and the piston into a suction side space and a discharge side space;
A first suction hole for sucking the working fluid into the suction side space of the first expansion mechanism;
a communication hole that connects the discharge side space of the kth expansion mechanism (k is an integer from 1 to n-1) and the suction side space of the (k + 1) th expansion mechanism to form one space;
a discharge hole for discharging the working fluid from the discharge side space of the nth expansion mechanism;
A connection position with the suction side space of the first expansion mechanism is variable, and a second suction hole for sucking the working fluid into the suction side space;
An expander is provided.

  The present invention also provides an expander-integrated compressor comprising an expander unit comprising the expander according to the present invention and a compressor unit integrally connected to the expander unit via the shaft. To do.

  Furthermore, the present invention provides a heat pump comprising the expander or the expander-integrated fluid machine according to the present invention.

  In the expander of the present invention, the timing of transition from the working fluid suction process to the working fluid expansion process is adjusted by changing the connection position between the suction side space of the first expansion mechanism and the second suction hole. The ratio of the length of time during which the expansion process is performed to the length of time during which the inhalation process is performed can be controlled. For this reason, according to the present invention, it is possible to change the above (Ves / Vcs). For example, in a refrigeration cycle using an expander-integrated compressor, it is possible to avoid the restriction of a constant density ratio. Therefore, it is possible to efficiently recover the expansion energy of the working fluid by supplying the entire amount of the working fluid to the expander without providing the subcircuit of the working fluid.

  When the expander of the present invention is used as a separation type expander, the rotation speed of the expander can be controlled while maintaining the amount of working fluid flowing into the expander. For this reason, it becomes easy to make the rotation speed of the generator connected to the expander near the rated rotation speed, and to maintain the power generation efficiency by the generator high.

The longitudinal cross-sectional view of the expander integrated compressor in the 1st Embodiment of this invention D1-D1 sectional drawing of the expander part of the expander integrated compressor of FIG. D2-D2 sectional view of the expander portion of the expander-integrated compressor of FIG. The partial cutaway perspective view of the fixing | fixed part of the upper end plate of the expander part of the expander integrated compressor of FIG. The perspective view of the movable part of the upper end plate of the expander part of the expander integrated compressor of FIG. Partial cutaway perspective view of the upper end plate integrating the fixed part and the movable part The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. Operational principle diagram of the first cylinder of the expander part of the expander-integrated compressor of FIG. Operational principle diagram of the second cylinder of the expander portion of the expander-integrated compressor of FIG. The figure which shows the relationship between the rotation angle of the shaft in the expander part of the expander integrated compressor of FIG. 1, and each stroke of a working chamber. The figure which shows the relationship between the rotation angle of the shaft in the expander part of the expander integrated compressor of FIG. 1, and a working chamber volume. Mollier diagram of refrigeration cycle using the expander-integrated compressor of FIG. PV diagram showing the relationship between pressure and working chamber volume in the expander section of the expander-integrated compressor of FIG. Configuration diagram of heat pump using expander integrated compressor Configuration diagram of a heat pump using a separate expander Graph illustrating the relationship between generator efficiency and generator speed The longitudinal cross-sectional view of the expander in the 2nd Embodiment of this invention D3-D3 sectional view of the expander of FIG. D4-D4 cross section of the expander of FIG. FIG. 11 is a configuration diagram of a heat pump including the expander and the pressure regulator in FIG. Cross section of actuator modification Configuration diagram of a modification of the pressure regulator Configuration of another modification of the pressure regulator The block diagram of the example which provides a pressure sensor in the pressure regulator of FIG. 16A Vertical section of an expander-integrated compressor according to a third embodiment of the present invention Cross section of rotary actuator D5-D5 sectional view of the rotary actuator of FIG. Configuration diagram of a heat pump using a conventional expander-integrated compressor Mollier diagram of a heat pump using a conventional expander-integrated compressor

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
1 is a longitudinal sectional view showing a configuration of an expander-integrated compressor according to a first embodiment of the present invention, and FIG. 2A is a cross-sectional view taken along a line D1-D1 of an expander portion of the expander-integrated compressor of FIG. 2B is a cross-sectional view taken along the D2-D2 cross section of the expander unit, FIG. 3A is a partially cutaway perspective view of a fixing portion of an upper end plate of the expander unit, and FIG. 3B is an upper end of the expander unit. FIG. 3C is a partially cutaway perspective view showing a state in which the fixed portion and the movable portion of the upper end plate are integrated.

  The expander-integrated compressor 100 according to this embodiment includes a hermetic container 11, a scroll-type compressor unit 20 disposed on the upper side, and a two-stage rotary type expander unit disposed on the lower side. 40, and the rotary motor 12 including the rotor 12a and the stator 12b disposed between the compressor unit 20 and the expander unit 40 are connected to the compressor unit 20, the expander unit 40, and the rotary motor 12. And a shaft 13. The shaft 13 may be formed by connecting a plurality of portions to one axis.

  The scroll-type compressor unit 20 includes a fixed scroll 21, an orbiting scroll 22, an Oldham ring 23, a bearing member 24, a muffler 25, a suction pipe 26, and a discharge pipe 27. The orbiting scroll 22 fitted to the eccentric shaft 13a of the shaft 13 and restrained by the Oldham ring 23 is rotated with the spiral wrap 22a meshing with the wrap 21a of the fixed scroll 21. Accordingly, the crescent-shaped working chamber 28 formed between the wraps 21a and 22a is reduced in volume while moving from the outside to the inside, thereby compressing the working fluid sucked from the suction pipe 26. . The compressed working fluid passes through a discharge hole 21b provided in the central portion of the fixed scroll 21, an inner space 25a of the muffler 25, and a flow path 29 penetrating the fixed scroll 21 and the bearing member 24 in this order, and is in a sealed container. 11 is discharged into the internal space 11a. The working fluid discharged to the inner space 11a is discharged from the discharge pipe 27 to the refrigeration cycle after the mixed lubricating oil is separated by gravity, centrifugal force, or the like while it stays in the inner space 11a.

  The two-stage rotary expander unit 40 includes a first cylinder 41, a second cylinder 42 that is thicker than the first cylinder 41, and an intermediate plate 43 that partitions the cylinders 41 and 42. The first cylinder 41 and the second cylinder 42 are arranged concentrically with each other. The expander unit 40 is further fitted to the eccentric portion 13 b of the shaft 13, and is held in a reciprocating manner in a first piston 44 that rotates eccentrically in the first cylinder 41 and a vane groove of the first cylinder 41. A first vane 46 with one end contacting the first piston 44, a first spring 48 contacting the other end of the first vane 46 and urging the first vane 46 toward the first piston 44; The second cylinder 42 is fitted to the eccentric portion 13c of the shaft 13, and is held in a reciprocating manner in a second piston 45 that rotates eccentrically in the second cylinder 42 and a vane groove of the second cylinder 42. A second vane 47 whose end is in contact with the second piston 45, and a second spring 49 which is in contact with the other end of the second vane 47 and biases the second vane 47 toward the second piston 45. ing.

  The first cylinder 41, the shaft 13, the first piston 44, and the first vane 46 constitute a first (first stage) expansion mechanism. Similarly, the second cylinder 42, the shaft 13, the second piston 45, and the second vane 47 constitute a second (second stage) expansion mechanism. The pistons 44 and 45 and the vanes 46 and 47 may be integrated (a so-called swing piston).

  The expander unit 40 further includes an upper end plate 73 and a lower end plate 51 disposed so as to sandwich the first and second cylinders 41 and 42 and the intermediate plate 43. The upper end plate 73 and the middle plate 43 sandwich the first cylinder 41 from above and below, and the middle plate 43 and the lower end plate 51 sandwich the second cylinder 42 from above and below. By holding the upper end plate 73, the middle plate 43 and the lower end plate 51, a working chamber whose volume changes in accordance with the rotation of the pistons 44 and 45 is formed in the first cylinder 41 and the second cylinder 42. The The upper end plate 73 and the lower end plate 51 are blocking members that close the cylinders 41 and 42, and also function as bearing members that rotatably hold the shaft 13 together with the bearing member 24 of the compressor unit 20. Similarly to the compressor unit 20, the expander unit 40 also includes a muffler 52, a suction pipe 53, and a discharge pipe 54.

  As shown in FIGS. 2A and 2B, inside the first cylinder 41, a suction side working chamber 55a (first suction side space) partitioned by a first piston 44 and a first vane 46 and a discharge side are provided. The working chamber 55b (first discharge side space) is disposed inside the second cylinder 42 by the second piston 45 and the second vane 47, and the suction side working chamber 56a (second suction side space) and the discharge. Side working chambers 56b (second discharge side spaces) are respectively formed. The total volume of the two working chambers 56 a and 56 b in the second cylinder 42 is larger than the total volume of the two working chambers 55 a and 55 b in the first cylinder 41. The discharge-side working chamber 55b of the first cylinder 41 and the suction-side working chamber 56a of the second cylinder 42 communicate with each other through a communication hole 43a provided in the intermediate plate 43, and one working chamber (expansion chamber) ). The high-pressure working fluid flows into the working chamber 55a and then expands to a low pressure while rotating the shaft 13 in the working chamber formed by the working chamber 55b and the working chamber 56a.

  As shown in FIG. 1, the upper end plate 73 includes a fixed portion 71 and a movable portion 72. As shown in FIG. 3A, the fixed portion 71 has a through hole 71 f for fitting the movable portion 72 together. The through-hole 71f has a cylindrical concave surface 71a, a cylindrical concave surface 71b having the same central axis 70 as the cylindrical concave surface 71a and having an inner diameter smaller than the cylindrical concave surface 71a, and a step surface 71c connecting the cylindrical concave surfaces 71a and 71b. being surrounded. When the fluid machine (expander-integrated compressor 100) is assembled, the central axis 70 coincides with the central axis of the shaft 13.

  Inside the fixed portion 71, as an inflow path for guiding the working fluid from the suction pipe 53 to the working chamber 55a, an inflow path 71d (first inflow path) and an inflow path 71e (first flow path) that is a branch path from the inflow path 71d. 2 inflow passages). As shown in FIGS. 1 and 2A, the first cylinder 41 is provided with an inflow path 41a and a first suction hole 41b as a flow path communicating with the inflow path 71e. One cylinder 41 communicates with a working chamber 55a on the suction side.

  As shown in FIG. 3B, the movable portion 72 of the upper end plate 73 has a through hole 72a for rotatably holding the shaft 13, and has a cylindrical convex surface that abuts on the cylindrical concave surface 71a of the fixed portion 71 as an outer peripheral surface. 72b, a cylindrical convex surface 72c that contacts the cylindrical concave surface 71b of the fixed portion 71, and a step surface 72g that contacts the step surface 71c of the fixed portion 71 between the cylindrical convex surfaces 72b and 72c. The cylindrical convex surface 72c of the movable portion 72 of the upper end plate 73 is provided with a gear 72e that goes around the cylindrical convex surface 72c in the circumferential direction. The movable portion 72 further includes a flow path groove 72d that circulates along the circumferential direction on the cylindrical convex surface 72b, and a second suction hole 72f connected to the flow path groove 72d. As shown in FIGS. 1 and 2A, the second suction hole 72f extends in the axial direction from the flow path groove 72d toward the working chamber 55a of the first cylinder 41, and the working chamber 55a on the suction side in the first cylinder 41. Communicating with

  As shown in FIG. 3C, the fixed portion 71 and the movable portion 72 are integrated by rotatably fitting the movable portion 71 into the through hole 71 f of the fixed portion 71. The stepped surface 71c of the fixed part 71 and the stepped surface 72g of the movable part 72 are in contact with each other to prevent the movable part 72 from slipping out above the fixed part 71. The lower end surface of the fixed portion 71 and the lower end surface of the movable portion 72 constitute the same plane, and this plane constitutes a partition above the first cylinder 41.

  When the movable portion 72 is rotated, the second suction hole 72f rotates and moves around the central axis 70 while maintaining a constant distance from the central axis 70 of the shaft 13. The rotation of the movable portion 72 causes a relative change in the position of the second suction hole 72 in the working chamber 55a on the suction side of the first cylinder 41. That is, while the connection position between the first suction hole 41b and the working chamber 55a on the suction side of the first cylinder 41 is fixed, the connection position between the second suction hole 72f and the working chamber 55a is variable. As will be described later, the change in the connection position of the second suction hole 72f makes it possible to avoid the restriction of a constant density ratio in the expander-integrated compressor.

  As described with reference to FIGS. 3A, 3B, and 3C, the second suction hole 72f is a blocking member that blocks the end surface of the first cylinder 41 included in the first fluid mechanism into which the working fluid first flows. The end plate 73 may be provided. This is because the movable second suction hole 72f can be configured with a simple configuration. Moreover, since the cylinder 41 side of the upper end plate 73 is a flat surface, it is easy to increase the processing accuracy even if the end plate 73 is constituted by a plurality of parts.

  In addition, as described above, it is preferable that at least a part of the end plate 73 is the movable portion 72 that can rotate around the shaft 13 and the second suction hole 72 f is provided in the movable portion 72. This is because it is easy to ensure a large movement range of the second suction hole 72f.

  Further, in the present embodiment, the movable portion 72 includes a cylindrical bearing surface that supports the shaft 13 (the inner peripheral surface of the through hole 72a). Therefore, it is not necessary to separately provide a bearing for supporting the shaft 13, thereby suppressing an increase in the number of parts.

  The fixed portion 71 has an annular shape, and an inflow passage 71d (first inflow passage) that supplies the working fluid from the outside of the expander portion 40 to the second suction hole 72f provided in the movable portion 72. An inflow path 71e (second inflow path) that branches from the inflow path 71d and supplies the working fluid to the first suction hole 41b is provided inside. The movable portion 72 is rotatably joined to such a fixed portion 71. Providing the two inflow passages 71d and 71e inside the fixed portion 71 eliminates the need for piping for guiding the working fluid to the second suction hole 72f, which is advantageous for space saving inside the sealed container 11. In addition, since the inflow passages 71d and 71e are provided in the fixed portion 71, the problem of leakage of the working fluid hardly occurs.

  Returning to FIG. 1, the description will be continued. The fixed portion 71 of the upper end plate 73 is further provided with a gear 75 that meshes with the gear 72 e of the rotating portion 72 and a rotary electric motor 76 (electric actuator) that drives the gear 75. The movable portion 72 is driven by a rotary electric motor 76 via gears 72e and 75. Thus, the expander unit 40 may further include drive mechanisms 75 and 76 that rotate the movable unit 72. The drive mechanisms 75 and 76 are connected to a controller (not shown) that is provided outside the sealed container 11 and controls the rotation angle of the movable part 72, and receives the control signal from the controller to move the movable part 72. Rotate to control the connection position to the working chamber 55a. If a stepping motor or a servo motor is used as the rotary electric motor 76, the position of the second suction hole 72f can be controlled with high accuracy. Further, a detector (for example, an encoder) that detects the rotation angle of the movable portion 72 may be provided. In addition, as a drive means of the movable part 72, means other than the rotary electric motor 76, for example, an actuator using a pressure difference of fluid may be used.

  The working fluid that has flowed into the expander section 40 from the suction pipe 53 is divided into two paths from the inflow path 71d of the fixing section 71 of the upper end plate 73 and flows into the working chamber 55a. The first path is a path that passes through the inflow path 71d in the fixed portion 71, the branch inflow path 71e, the inflow path 41a in the first cylinder 41, and the first suction hole 41b. The second path is a path that passes through the inflow path 71d in the fixed part 71, the flow path groove 72d of the movable part 72, and the second suction hole 72f. As described above, in the expander unit 40, the connection position between the first suction hole 41b in which the connection position with the working chamber 55a is fixed from the intake pipe 53 to the first working chamber 55a and the working chamber 55a are variable. The working fluid is supplied via the second suction hole 72f. In these two paths, there is no need to arrange a flow rate control mechanism such as an electromagnetic valve or a differential pressure valve that can be opened and closed.

  The working fluid sucked into the first cylinder 41 passes through the second cylinder 42, passes through the discharge hole 51 a provided in the lower end plate 51, the inner space 52 a of the muffler 52, and the first and second cylinders 41 and 42. It discharges from the discharge pipe 54 to the refrigerating cycle via the flow path 57 which penetrates in this order. The discharge hole 51a may be provided in the second cylinder 42.

  As shown in FIG. 2B, a discharge valve 74 is installed in the discharge hole 51 a provided in the lower end plate 51. The discharge valve 74 is made of, for example, a metal thin plate, and is disposed so as to close the discharge hole 51 a from the inner space 52 a side of the muffler 52. The discharge valve 74 is a differential pressure valve that opens when the pressure on the upstream side (the working chamber 56b side on the discharge side of the second cylinder 42) becomes higher than the pressure on the downstream side (the inner space 52a side of the muffler 52). The discharge valve 74 has a function of preventing overexpansion of the working fluid in the expander unit 40.

  4A, 4B, and 4C show the positions of the first suction hole 41b and the second suction hole 72f. The position of the second suction hole 72f is indicated by an angle φ with reference to the position of the first vane 46 around the shaft 13, and is 20 ° (FIG. 4A), 90 ° (FIG. 4B), 180 ° (FIG. 4C), respectively. More precisely, the angle φ is a rotational direction of the shaft 13 about the center axis 70 (illustrated) with respect to the first straight line 80 connecting the contact point between the first vane 46 and the first piston 44 and the center axis 70 of the shaft 13. (Clockwise in this example) is an angle when rotating to the second straight line 90 connecting the second suction hole 72f and the central axis 70 of the shaft 13. According to this notation method, in the illustrated example, the first suction hole 41b is fixed at a position of 20 °. Further, the discharge hole 51a is fixed at a position of 340 ° in the same notation in the second cylinder. On the other hand, the position of the second suction hole 72f can be arbitrarily set between 0 ° and 360 °.

  FIG. 5A shows an operation principle diagram of the first cylinder 41 when the angle φ of the second suction hole 72f is 90 °, and FIG. 5B shows an operation principle diagram of the second cylinder 42 corresponding to the above. Here, the rotation angle θ of the shaft 13 is set to 0 ° when the contact point between the first cylinder 41 and the first piston 44 is at a so-called top dead center located in the first vane 46, and in the rotation direction of the shaft 13. A certain clockwise direction is displayed as positive.

  The working fluid flows into the working chamber 55a generated after θ = 0 ° from the first suction hole 41b after θ = 20 °. After θ = 90 °, the working fluid flows into the working chamber 55a from the first suction hole 41b and the second suction hole 72f. After θ = 360 °, the working chamber 55a changes to the working chamber 55b and communicates with the working chamber 56a of the second cylinder 42 through the communication hole 43a. When the shaft 13 further rotates, at θ = 380 ° (not shown), the contact point between the first cylinder 41 and the first piston 44 passes through the first suction hole 41b, and the working chamber 55b, the first suction hole 41b, Is disconnected. In the conventional two-stage rotary expander unit, the working fluid suction process ends at this point.

  On the other hand, since the second suction hole 72f is provided in the expander unit 40 of the present embodiment, the inflow of the working fluid from the second suction hole 72f continues even when θ = 380 °. In this expander section 40, θ = 450 °, and the contact between the first cylinder 41 and the first piston 44 passes through the second suction hole 72f, and the communication between the working chamber 55b and the second suction hole 72f is cut off. At that time, the working fluid suction process ends.

  When the suction process is completed, the working fluid expansion process is started. When the shaft 13 further rotates, the volume of the working chamber 55b decreases. However, since the second cylinder 42 is higher in the axial direction and has a larger volume than the first cylinder 41, the volume of the working chamber 56a is larger than that. To increase. As a result, as the shaft 13 rotates, the sum of the volumes of the working chamber 55b and the working chamber 56a increases, and the working fluid expands. When θ = 700 ° (not shown), the contact between the second cylinder 42 and the second piston 45 passes through the discharge hole 51a, and the working chamber 56a communicates with the discharge hole 51a. At this point, the expansion process ends.

  When the expansion process is finished, the discharge process of the working fluid is started. At θ = 720 °, the working chamber 55b disappears, the working chamber 56a changes to the working chamber 56b, and further, as the shaft 13 rotates, the volume of the working chamber 56b decreases and the working fluid is discharged from the discharge hole 51a. . When θ = 1080 °, the working chamber 56b disappears, and the discharge process ends.

  FIG. 6A shows the relationship between the rotation angle θ of the shaft 13 and the transition point of each process from suction to discharge when the angle φ of the second suction hole 72f is 20 °, 90 °, and 180 °. As is clear from the above description, the rotation angle θ of the shaft 13 at which the suction process ends is an angle when the contact point between the first cylinder 41 and the first piston 44 passes through the second suction hole 72f for the second time. . This angle can be expressed as θ = (360 + φ). Therefore, as the angle φ of the second suction hole 72f increases, the timing of transition from the suction process to the expansion process is delayed, the suction process is lengthened, and the expansion process is shortened. That is, the ratio of the length of time during which the expansion process is performed to the length of time during which the inhalation process is performed becomes small.

  FIG. 6B shows the relationship between the rotation angle θ of the shaft 13 and the working chamber volume. The working fluid moves in the order of the working chamber 55a, the working chamber 55b, the working chamber 56a, and the working chamber 56b. In this process, the volume of the working chamber changes in a sinusoidal curve. On the vertical axis in the figure, the suction volume Vesφ that is the volume of the working chamber at the end of the suction process when the angle φ of the second suction hole 72f is 20 °, 90 °, and 180 °, and the working chamber at the start of the discharge process The discharge volume Ved which is the volume of is shown. The suction volume Vesφ increases as φ increases, but the discharge volume Ved is constant regardless of φ.

  As described above, in this embodiment, in addition to the fixed first suction hole 41b provided in the conventional two-stage rotary expander unit 40, the movable second suction hole 72f is provided, The suction volume Vesφ that is the volume at the end of the suction process of the working chambers 55a, 55b, 56a, and 56b was made variable. Thereby, the density ratio (Vcs / Vesφ) of the working fluid on the inlet side of the compressor unit 20 and the expander unit 40 can be controlled.

  In FIG. 7, the Mollier diagram of the refrigerating cycle using the expander integrated compressor of this embodiment is illustrated. Since the density ratio can be changed, only the pressure is changed along the isotherm (T = 35 ° C. in the illustrated example) at the point C corresponding to the state on the inlet side of the two-stage rotary expander unit 40. Thus, the temperature and pressure on the inlet side of the two-stage rotary expander unit 40 can be freely controlled, and the conventional expander can be moved to the point C ′ or the point C ″. An efficient refrigeration cycle operation, which was impossible with a refrigeration cycle using a body compressor, is possible.

  In particular, as in the present embodiment, when the second suction hole 72f is formed in the movable portion 72 that can rotate around the axis of the shaft 13, and the angle φ can be adjusted from 0 ° to 360 °, the control is performed. Since the width is large, it is easy to improve the efficiency of the refrigeration cycle.

  Next, the effect obtained by providing the discharge valve 74 in the discharge hole 51a will be described. FIG. 8 shows the relationship between the volume of the working chamber and the pressure (PV diagram). The subscript φ of the symbol in the figure is the angle φ of the second suction hole 72f. Point Pφ represents the start of the expansion process, point Sφ represents the end of the expansion process, and point T represents the start of the discharge process. Since a refrigeration cycle using carbon dioxide as a working fluid is assumed, the inflection point Qφ due to the phase change is shown during the expansion process.

Since the discharge volume Ved is constant, the volume ratio (= Ved / Vesφ) before and after the expansion process decreases as the suction volume Vesφ increases with the movement of the second suction hole 72f, and the pressure at the end of the expansion process Sφ increases. Therefore, for example, when the range of the angle φ of the second suction hole 72f is controlled in the range of 20 ° to 180 °, the pressure S ₁₈₀ at the end of the expansion process when the maximum angle 180 ° is selected is the low pressure of the refrigeration cycle. It is desirable to set the pressure so as to be lower than the side pressure Ped so that underexpansion does not occur. This is because when the underexpansion occurs, a part of energy due to the pressure difference of the working fluid cannot be recovered.

  With this design, overexpansion occurs at least when the angle φ is set to 180 ° or less. Overexpansion is a phenomenon in which the pressure Pedφ is lower than the low pressure side pressure Ped of the refrigeration cycle. When the overexpansion occurs, an overexpansion loss is generated in the discharge process because the working fluid is pushed out from the discharge hole 51a into the inner space 52a of the muffler 52 having a pressure higher than that in the working chamber 56b. The magnitude of the overexpansion loss can be indicated by the area of the triangle RφSφT in FIG.

  However, if the discharge valve 74 is provided in the discharge hole 51a, if overexpansion CφDφ occurs in the working chamber 56b, recompression is performed in the discharge process. In the discharging process, the working chamber 56b becomes smaller in volume as the shaft 13 rotates. If the discharge valve 74 is disposed in the discharge hole 51a, the discharge valve 74 is not opened until the pressure in the working chamber 56b, which has been reduced due to overexpansion, becomes equal to the low-pressure side pressure Pd of the refrigeration cycle. Will be recompressed. Thus, if the discharge valve 74 is arranged, an overexpansion loss can be prevented.

  Hereinafter, other features of the expander-integrated compressor of the present embodiment will be described.

  In the present embodiment, it is preferable that the movable portion 72 of the upper end plate 73 provided with the second suction hole 72f is rotatable about the shaft 13 in the same direction as the rotation direction of the shaft 13. This is because the movable portion 72 can be rotated with a small amount of power by the frictional force between the shaft 13 and the movable portion 72. According to this, it becomes easy to reduce the size of the rotary electric motor 76 and store it in the sealed container 11.

  In this embodiment, if the movable part 72 rotates 360 degrees, it returns to the original position. For this reason, the movable part 72 has only to be rotated in the same direction at all times, and the control of the rotary motor 76 is simple. The frictional force between the shaft 13 and the movable part 72 does not hinder the rotational drive.

  In this embodiment, since the suction volume Vesφ of the expander unit 40 is variable, the compressor unit 20 has a normal structure used for a refrigeration cycle that does not use an expander. About the compressor part 20, since a normal structure can be used as it is, development cost can be reduced.

  When the expander-integrated compressor of the present embodiment is used, the expander unit 40 rotates at the same rotational speed as the compressor unit 20 while controlling the circulation amount of the working fluid in the refrigeration cycle by the rotational speed of the compressor unit 20. The suction volume Vesφ can be adjusted according to the operating conditions. Therefore, it is possible to share the role of the compressor unit 20 and the expander unit 40 in controlling the refrigeration cycle, and the control algorithm of the refrigeration cycle using the expander-integrated compressor is facilitated.

  Although there is no restriction | limiting in the kind of working fluid used for the expander integrated compressor of this embodiment, Carbon dioxide is suitable. This is because the effect of power recovery by the expander becomes more prominent. For this reason, when the working fluid is carbon dioxide, the effect of increasing the efficiency by avoiding the constant density ratio becomes remarkable.

  In the present embodiment, the second suction holes 72f that are movable together with the first suction holes 41b are provided. However, the number of movable suction holes may be two or more, and in this case, the most downstream position is provided. The suction volume Vesφ is determined by the suction hole arranged at the bottom. Further, in this embodiment, the expander unit 40 has two stages, but even when there are three or more stages, the same effect as described above can be obtained by providing the second suction hole that can move with respect to the first-stage cylinder. Can be obtained.

  Next, FIG. 9A shows a configuration of a power recovery type heat pump using the expander-integrated compressor of the present embodiment. The heat pump shown in FIG. 9A includes an expander-integrated compressor 100, a gas cooler (heat radiator) 2, an evaporator 4, and a pipe 88 (refrigerant pipe) that connects them to each other. In the conventional example shown in FIG. 20, the sub-circuit 9 connected in parallel to the expander 3 is indispensable. However, in the heat pump using the expander-integrated compressor of this embodiment, such a sub-circuit is essentially included. Is unnecessary. However, a sub-circuit may be provided for other purposes, for example, for the purpose of stably starting and stopping the heat pump.

  Furthermore, the expander unit 40 of the present embodiment may be used alone, that is, as an expander separated from the compressor. FIG. 9B shows a configuration of a power recovery type heat pump using a separation type expander. This apparatus includes a compressor 81, a gas cooler (heat radiator) 82, an expander 83, and an evaporator 84. Further, the compressor 81, the gas cooler 82, the expander 83, and the evaporator 84 are connected in this order, and the working fluid circulates. A pipe body 88 (refrigerant pipe) is provided. The expander 83 includes the expander unit 40 described with reference to FIG. In this heat pump, the expansion energy of the working fluid obtained by the expander 83 is converted into electric energy by the generator 86 and used as part of the input of the rotary motor 85 that rotates the compressor 81.

  FIG. 10 shows an efficiency curve of a general generator 86. Since the generator 86 is designed to have the highest power generation efficiency at a predetermined rated rotational speed Nr, the power generation efficiency decreases as the rotational speed goes away from the rated rotational speed. For this reason, it is desirable that the rotational speed of the generator 86 be as close to the rated rotational speed Nr as possible. However, in the refrigeration cycle, since the circulation amount and density of the working fluid change, it is difficult to operate only in the vicinity of the rated rotation speed Nr with an expander having a constant suction volume Ves. If the expander unit 40 of the first embodiment is used as the expander 83, the rotation speed can be controlled to be close to the rated rotation speed Nr by adjusting the suction volume Vesφ.

(Second Embodiment)
As mentioned in the previous embodiment, the position of the second suction hole for changing the suction volume of the expander can also be changed by an actuator that uses the pressure difference of the fluid. According to the actuator using the pressure difference of the fluid, the reliability is high under a severe environment such as high temperature and high pressure. Further, there is an advantage that the working fluid to be expanded by the expander can be used as it is for the power source of the actuator. In the present embodiment, a variable suction volume expander including such an actuator will be described. In the present embodiment, the same reference numerals are used for the same components as those described in the first embodiment.

  FIG. 11 is a longitudinal sectional view of an expander according to the second embodiment. As shown in FIG. 11, the expander 303 is a rotary expander. The expander 303 includes a sealed container 11, a generator 86 arranged in the sealed container 11, and an expander unit 400 connected to the generator 86. The expander unit 400 includes a port member 412b (movable member), a housing 413 that houses the port member 412b, and an actuator 406.

  The port member 412b closes the cylinder 41 (first cylinder) of the first expansion mechanism, and can rotate independently of the shaft 13 with the shaft 13 as a rotation center. The port member 412b is provided with an additional second suction hole 412c. The actuator 406 is a fluid pressure actuator using a pressure difference between fluids as a power source, and applies a rotational force having a magnitude based on the pressure difference between the high pressure fluid and the low pressure fluid to the port member 412b. When the rotation angle of the port member 412b around the central axis O is switched, the position of the second suction hole 412c changes. As a result, in the expander unit 400, the timing of transition from the working fluid suction process to the expansion process changes, and the ratio of the length of time during which the expansion process is performed to the length of time during which the suction process is performed changes.

  The working fluid to be expanded by the expander 303 can be used as the high-pressure fluid and low-pressure fluid that are the power source of the actuator 406. In this way, it is not necessary to separately prepare a fluid for operating the actuator 406. In addition, a strict seal structure that prevents mixing of different fluids is unnecessary. The mechanism for using the working fluid as a power source for the actuator 406 will be clarified by the following description.

  In the present embodiment, the actuator 406, the port member 412b, and the cylinder 41 (first cylinder) of the first expansion mechanism are arranged in this order and concentrically in a direction parallel to the central axis O of the shaft 13. ing. Such an arrangement is advantageous for a small expander 303 because it is possible to suppress the size expansion caused by newly providing the actuator 406 and the port member 412b as much as possible.

Hereinafter, each part of the expander 303 will be described individually.
The generator 86 includes a stator 86b fixed to the side wall of the hermetically sealed container 11 and a rotor 86a disposed inside the stator 86b. The shaft 13 is fixed to the center of the rotor 86a. The shaft 13 extends downward from the rotor 13 a and is shared by the expander unit 400.

  An oil reservoir 405 for storing lubricating oil is formed at the bottom of the sealed container 11. The lower end portion of the shaft 13 is disposed in the oil sump 405. An oil pump (not shown) is formed at the lower end of the shaft 13, and an oil supply passage (not shown) is formed inside and / or the outer periphery of the shaft 13. When the shaft 13 rotates, the lubricating oil in the oil reservoir 405 is pumped up by the oil pump and supplied to the sliding portions of the expander unit 400 through the oil supply passage.

  Since the basic structure of the expander unit 400 and the mechanism for expanding the working fluid are as described in the first embodiment, they are omitted here. Note that an actuator 406 and a port member 412b for changing the position of the second suction hole 412c are disposed between the upper end plate 424 as a bearing member and the first cylinder 41, and the first cylinder 41. This embodiment is different from the first embodiment in that the end face is closed by the port member 412b.

  Hereinafter, the port member 412b and the actuator 406 will be described in detail. The port member 412 b has a substantially disk shape with a hole through which the shaft 13 passes in the center, and is disposed inside the housing 413 whose outer shape substantially coincides with the first cylinder 41. The inner diameter of the housing 413 and the outer diameter of the port member 412b are substantially equal, and the displacement of the port member 412b in the radial direction is restricted by the housing 413. However, the port member 412b can smoothly rotate inside the housing 413. A second suction hole 412c is formed in the port member 412b so as to penetrate vertically in the axial direction at a position not overlapping with the piston 430 of the actuator 406. As the port member 412 b rotates, the second suction hole 412 c moves in the rotation direction of the shaft 13.

  12A is a cross-sectional view of the expander shown in FIG. 11 taken along the line D3-D3. As shown in FIG. 12A, the actuator 406 includes a port member driving eccentric portion 412a, a port member driving piston 430, a port member driving cylinder 432, a port member driving vane 433, a port member driving spring 434, and a suction pipe 53. And a control pressure pipe 435. The shaft 13 is located at the center of the port member driving cylinder 432.

  In the following description, the term “port member driving” is omitted for the sake of brevity regarding each component of the actuator 406.

  As shown in FIG. 12A, the eccentric portion 412 a is eccentric with respect to the shaft 13 and is disposed inside the cylinder 432. The upper side of the cylinder 432 is closed by an upper end plate 424 (see FIG. 11). The piston 430 is fitted into the eccentric portion 412a so as to form a pressure chamber 431 (431a, 431b) between the piston 430 and the cylinder 432. The eccentric portion 412a and the piston 430 rotate (specifically, eccentrically swing) in the cylinder 432 while maintaining an eccentric state with respect to the central axis O of the shaft 13. A through hole through which the shaft 13 passes is formed in the eccentric portion 412a. The eccentric part 412a and the shaft 13 are not joined and can rotate independently of each other.

  The vane 433 is reciprocally held in a vane groove provided in the cylinder 432 so that the tip thereof is in contact with the piston 430. The spring 434 biases the vane 433 toward the piston 430.

  The pressure chambers 431a and 431b formed inside the cylinder 432 are separated by a vane 433 into two spaces of a first pressure chamber 431a and a second pressure chamber 431b. Further, the cylinder 432 is provided with a high pressure side inflow hole 450 and a low pressure side inflow hole 451. The high pressure side inflow hole 450 and the low pressure side inflow hole 451 are separated from each other by a predetermined angle in the circumferential direction, and penetrate through the inside and outside of the cylinder 432. A suction pipe 53 is connected to the first pressure chamber 431a via a high-pressure side inflow hole 450. The suction pipe 53 supplies a high-pressure working fluid before expansion to the first pressure chamber 431a. A control pressure pipe 435 is connected to the second pressure chamber 431b through a low pressure side inflow hole 451. The control pressure pipe 435 supplies a working fluid having a pressure lower than that of the working fluid supplied to the first pressure chamber 431a to the second pressure chamber 431b. The differential pressure between the first pressure chamber 431a and the second pressure chamber 431b gives a rotational force to the piston 430. The piston 430 that receives the rotational force from the differential pressure of the working fluid rotates the eccentric portion 412a and the port member 412b.

  Also, the cylinder 432 passes through the upper end plate 424 from the suction pipe 53, passes through the cylinder 432, the housing 413, and the first cylinder 41 to suck the working fluid into the working chamber 55 a of the first cylinder 41. A suction passage 437 is formed.

  That is, the expander unit 400 in the expander 303 of the present embodiment is connected to the first suction hole 41b formed in the first cylinder 41, and the suction path for sending the working fluid (refrigerant) to the first cylinder 41. 437 and a high-pressure side inflow hole 450 as a branch path branched from the suction path 437. The high-pressure chamber 431a of the actuator 406 and the high-pressure side inflow hole 450 are connected, and the high-pressure working fluid supplied to the actuator 406 through the high-pressure side inflow hole 450 is used as the high-pressure fluid for driving the actuator 406. Further, the actuator 406 and the port member 412b are arranged adjacent to each other so that one end of the second suction hole 412c provided in the port member 412b is connected to the high pressure chamber 431a of the actuator 406, and as a high pressure fluid The working fluid supplied to the actuator 406 is supplied to the working chamber 55a (see FIG. 2A) in the first cylinder 41 through the second suction hole 412c provided in the port member 412b.

  In this way, it is not necessary to separately prepare a fluid for operating the actuator 406. A strict seal structure that prevents mixing of different types of fluids is not necessary, and the problem that the characteristics of the refrigeration cycle change due to mixing of different types of fluids does not occur. Further, by using the working fluid used in the expander 303 as a power source for the actuator 406, it is not necessary to supply energy such as electric power from the outside, which is advantageous in improving the recovery efficiency of the working fluid expansion energy.

  On the inner peripheral surface of the cylinder 432, a first stop 436a and a second stop 436b having a convex shape toward the central axis O of the shaft 13 are provided at a predetermined angle in the circumferential direction. These stops 436a and 436b have a pressure difference between the piston 430 and the working fluid (when the working fluid (refrigerant) is carbon dioxide, at a rated operation, the high pressure side has a pressure exceeding about 10 MPa and the low pressure side has a pressure of about 3 to 5 MPa. ) To limit the movable range (rotation angle around the central axis O) when rotating. As a result, the port member 412b is only allowed to rotate within a range of a predetermined angle (for example, about 180 °).

  Note that the rotation center of the piston 430 of the actuator 406 may coincide with the rotation center of the shaft 13. However, if the structure in which the piston 430 rotates eccentrically as in the present embodiment is adopted, the space for forming the second suction hole 412c penetrating the port member 412b up and down can be secured with a margin, and the expander can be downsized. Is also advantageous.

  12B is a cross-sectional view taken along line D4-D4 of the expander 303 shown in FIG. As shown in FIG. 12B, a rotation spring 439 (biasing means) is attached to the port member 412b. The rotary spring 439 is preferably incorporated in the port member 412b. The rotation spring 439 is interposed between the port member 412b and the housing 413 (or the cylinder 432), and always urges the port member 412b, the eccentric portion 412a, and the piston 430 in a predetermined rotation direction. As shown in FIG. 12A, in the present embodiment, since the first pressure chamber 431a is on the high pressure side and the second pressure chamber 431b is on the low pressure side, the biasing direction of the rotary spring 439 is determined according to the volume of the first pressure chamber 431a. The decreasing direction, that is, the position of the second suction hole 412c approaches the first suction hole 41b (see FIG. 2A). By such an action of the rotary spring 439, the position of the port member 412b can be continuously changed within the movable range determined by the stops 436a and 436b. Further, the port member 412b can be rotated in both forward and reverse directions under the relationship that the working fluid supplied to the first pressure chamber 431a is high pressure and the working fluid supplied to the second pressure chamber 431b is low pressure.

  Of course, even if the rotary spring 439 is not provided, if the magnitude relationship between the pressure of the working fluid supplied to the first pressure chamber 431a and the pressure of the working fluid supplied to the second pressure chamber 431b is reversed, The port member 412b can be rotated in both forward and reverse directions. By providing the stops 436a and 436b, the rotation range of the port member 412b can be limited. However, in such a configuration, it becomes difficult to use the working fluid used in the expander 303 as a power source for the actuator 406, resulting in a complicated structure. Therefore, it is preferable to use this embodiment.

  Further, according to the rotary spring 439 as described above, the magnitude of the rotational force applied to the piston 430 changes according to the position occupied by the piston 430 in the cylinder 432. The forward (or reverse) rotational force that the differential pressure between the high pressure working fluid supplied to the first pressure chamber 431a and the low pressure working fluid supplied to the second pressure chamber 431b gives to the eccentric portion 412a and the piston 430, The repulsive force by the rotation spring 439, that is, the reverse direction (or forward direction) rotational force applied to the port member 412b is balanced, so that the port member 412b is positioned at a predetermined rotational angle. In this way, by controlling the differential pressure between the working fluid supplied to the first pressure chamber 431a of the actuator 406 and the working fluid supplied to the second pressure chamber 431b, the control to freely displace the port member 412b. Is possible. That is, the second suction hole 412c can be adjusted to an optimum position according to the operating condition of the expander 303.

  As described above, the high-pressure working fluid flows from the suction pipe 53 through the suction passage 437 and flows into the working chamber 55a (see FIG. 2A) from the first suction hole 41b provided in the first cylinder 41. Separately from the path, the high-pressure working fluid flows into the first pressure chamber 431a inside the cylinder 432 via the high-pressure side inflow hole 450 branched from the suction pipe 53, and the second suction fluid provided in the port member 412b. It flows into the working chamber 55a through the hole 412c. As the port member 412b rotates, the position of the second suction hole 412c changes, so that the suction volume of the working fluid to the first cylinder 41 changes.

  In this embodiment, the port member driving eccentric portion 412a and the port member 412b are connected or integrated in the vertical direction parallel to the central axis O. As shown in FIGS. 11 and 12B, the port member 412b has a substantially disk shape, and closes the first cylinder 41 on one main surface, and the port member driving eccentricity on the other main surface side. The port member driving cylinder 432 is closed by being connected (or integrated) with the portion 412a. A portion located on the side farther from the first cylinder 41 is the port member driving eccentric portion 412a, and a portion located on the side closer to the first cylinder 41 is the port member 412b. In this way, the power transmission mechanism from the actuator 406 to the port member 412b can be omitted, which contributes to the suppression of the increase in the number of parts and the simplification of the structure, as well as the highly reliable expander 303. . The port member driving eccentric portion 412a itself can also serve as the port member driving piston 430. In this case, the port member 412b is configured as a part integrated with the port member driving piston 430. can do.

  The positional relationship between the first suction hole 41b and the second suction hole 412c is as described in FIGS. 4A, 4B, and 4C.

  Further, the operation principle of the first cylinder 41 and the second cylinder 42 is as described in FIGS. 5A and 5B.

  The relationship between the rotation angle θ of the shaft 13 and the transition point of each process from suction to discharge is as described with reference to FIG. 6A.

  Further, the relationship between the rotation angle θ of the shaft 13 and the working chamber volume is as described in FIG. 6B.

  Next, a pressure regulator for controlling the pressure of the working fluid supplied to the control pressure pipe 435 of the actuator 406 will be described. A heat pump 300 shown in FIG. 13 includes a compressor 81, a gas cooler 82, the expander 303 described with reference to FIG. 11, an evaporator 84, and a pressure regulator 500A. The pressure regulator 500A adjusts the differential pressure between the high pressure fluid and the low pressure fluid to be supplied to the actuator 406 of the expander 303. By providing such a pressure regulator 500A, the operation of the actuator 406 can be controlled from the outside of the expander 303. In the example of FIG. 13, the pressure regulator 500 </ b> A is installed outside the expander 303, but can be installed inside the expander 303.

  The pressure regulator 500A includes a first pressure pipe 501 having one end connected to the suction pipe 53 of the expander 303, a second pressure pipe 502 having one end connected to the control pressure pipe 435 of the expander 303, and the expander 303. A third pressure pipe 503 having one end connected to the discharge pipe 54 and a hollow housing 513 to which the other ends of the pressure pipes 501, 502, and 503 are connected are provided. That is, the outlet pipe of the radiator 302 is branched into the first pressure pipe 501 and the suction pipe 53 of the expander 303. Further, the discharge pipe 54 and the third pressure pipe 503 of the expander 303 are joined to form an inlet pipe of the evaporator 304. The interior of the housing 513 is partitioned into three pressure adjustment chambers, a first pressure adjustment chamber 504, a second pressure adjustment chamber 505, and a third pressure adjustment chamber 506. A first pressure pipe 501 is connected to the first pressure adjustment chamber 504. A second pressure pipe 502 is connected to the second pressure adjustment chamber 505. A third pressure pipe 503 is connected to the third pressure adjustment chamber 506.

  An elastic body 507 (spring) is disposed in the third pressure adjustment chamber 506. Between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506, there is disposed a piston 508 that partitions both pressure adjustment chambers and one end of which is connected to the elastic body 507. The piston 508 can advance and retreat between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506. The piston 508 is formed with a fine channel 514 that communicates the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506. Between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505, a valve 509 for adjusting the amount of working fluid flowing between the two pressure adjustment chambers is provided. One end of a connecting shaft 512 is connected to the valve 509. The other end of the connecting shaft 512 is connected to the iron core 511. A coil 510 is disposed around the iron core 511. The iron core 511 and the coil 510 constitute a plunger type solenoid.

  In the pressure regulator 500A, the first pressure regulation chamber 504 is equal to the pressure on the high pressure side of the refrigerant circuit, and the third pressure regulation chamber 506 is equal to the pressure on the low pressure side of the refrigerant circuit. Further, the pressure in the second pressure regulation chamber 505 controlled by the pressure regulator 500A is supplied to the control pressure pipe 435 of the expander 303 and used to change the suction volume of the expander unit 400.

  In the configuration as shown in FIG. 13, the connecting shaft 512 has an elastic restoring force of the elastic body 507, a pressure due to the pressure difference between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506, and a current flowing through the coil 510. The driving force given is added. The connecting shaft 512 stops at a position where these forces are balanced. By changing the current flowing through the coil 510, the pressure in the second pressure regulation chamber 505 can be controlled.

  That is, the pressure regulator 500A acquires a part of the high-pressure working fluid to be sent to the first suction hole 41b of the expander unit 400, and depressurizes the obtained working fluid to thereby reduce the second pressure chamber 431b of the actuator 406. Create a low-pressure working fluid to supply to Then, the pressure of the second pressure chamber 431b formed in the port member driving cylinder 432 is controlled by adjusting the degree of decompression of the working fluid, and is provided in the port member 412b and the port member 412b around the central axis O. The position of the second suction hole 412c is controlled. In this way, the position of the second suction hole 412c can be controlled easily and accurately.

  Thus, the heat pump 300 has one end connected to the main pipe (suction pipe 53) for sending the working fluid to the first suction hole 41b of the expander unit 400, and the other end connected to the pressure regulator 500A. One end is connected to the first pressure pipe 501 that supplies a part of the high-pressure working fluid to be supplied to the first pressure adjustment chamber 504 of the pressure regulator 500A, and the second pressure adjustment chamber 505 of the pressure regulator 500A. Is connected to the actuator 406 (specifically, the control pressure pipe 435), and a second pressure pipe 502 that supplies the low-pressure working chamber 431b (see FIG. 14) of the actuator 406 to the low-pressure working fluid decompressed by the pressure regulator 500A; It has.

  The operation of the pressure regulator 500 will be described. For example, when it is desired to increase the suction volume of the expander 303 (expander unit 400), the current flowing through the coil 510 is increased. Then, the force in the direction of the elastic body 507 acting on the iron core 511 increases, the elastic body 507 is contracted, and the valve 509 narrows the passage between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505. As a result, the pressure in the second pressure adjustment chamber 505 decreases and approaches the pressure in the third pressure adjustment chamber 506. Accordingly, the differential pressure between the pressure in the control pressure pipe 435 and the pressure in the suction pipe 53 increases. The port member driving piston 430 and the port member driving eccentric portion 412a rotate in a direction in which the volume of the second pressure chamber 431b decreases. The second suction hole 412c arrives at the position shown in FIG. 4C, for example. As a result, the suction time of the expander 303 is lengthened and the suction volume is increased according to the principle described in FIGS. 5A and 5B.

  Conversely, when it is desired to reduce the suction volume of the expander 303 (expander unit 400), the current flowing through the coil 510 is decreased. Then, the force in the direction of the elastic body 507 acting on the iron core 511 decreases, the length of the elastic body 507 increases, and the valve 509 widens the passage between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505. As a result, the pressure in the second pressure adjustment chamber 505 increases and approaches the pressure in the first pressure adjustment chamber 504. Accordingly, the differential pressure between the pressure in the control pressure pipe 435 and the pressure in the suction pipe 53 decreases. The port member driving piston 430 and the port member driving eccentric portion 412a rotate in a direction in which the volume of the second pressure chamber 431b increases. The second suction hole 412c arrives at the position shown in FIG. 4A, for example. As a result, the suction time of the expander 303 is shortened and the suction volume is reduced according to the principle described in FIGS. 5A and 5B.

  It is also possible to employ a pressure regulator configured as shown in FIG. First, as shown in FIG. 14, a fine passage 440 that bypasses the control pressure pipe 435 and the suction pipe 53 is provided in the actuator 406 ′. As shown in FIG. 15, the pressure regulator 500B includes a housing 515, a coil 510, an iron core 511, a connecting shaft 512, a piston 516, and an elastic body 507 (spring). The interior of the housing 515 is partitioned into two pressure adjustment chambers 520 and 521. A valve 509 that adjusts the amount of working fluid flowing between the two adjusting chambers is disposed between the two pressure adjusting chambers 520 and 521. The coil 510 and the iron core 511 constitute a plunger type solenoid. The elastic body 507 biases the valve 509 in a direction to open through the piston 516. On the other hand, when a current is passed through the coil 510, the iron core 511 biases the valve 509 in a closing direction via the connecting shaft 512. That is, the opening degree of the valve 509 can be controlled by controlling the current flowing through the coil 510. According to the opening degree of the valve 509, the pressure in the pressure adjusting chamber 521 to which the control pressure pipe 435 is connected can be changed.

  In the examples of FIGS. 13 and 15, it is necessary to keep the control pressure by constantly flowing the working fluid little by little, and the recovery efficiency of the expansion energy is inevitably lowered. Therefore, if the control pressure is made with the configuration shown in FIG. 16A, the recovery efficiency of the expansion energy can be further increased.

  A pressure regulator 500C illustrated in FIG. 16A includes a housing 560 that is partitioned into three pressure regulation chambers, a first pressure regulation chamber 561, a second pressure regulation chamber 562, and a third pressure regulation chamber 563. Yes. A first pressure pipe 501 through which the working fluid before expansion flows is connected to the first pressure adjustment chamber 561. Connected to the second pressure adjustment chamber 562 is a second pressure pipe 502 that communicates the second pressure adjustment chamber 562 and the second pressure chamber 431 b (see FIG. 12A) of the actuator 406 in the expander 303. A third pressure pipe 503 through which the expanded working fluid flows is connected to the third pressure adjustment chamber 563. A first valve 580 is disposed between the first pressure adjustment chamber 561 and the second pressure adjustment chamber 562. The first valve 580 can be controlled to open and close by driving a plunger type solenoid constituted by the coil 570, the iron core 573, the elastic body 584 (spring), and the connecting shaft 576. By opening the first valve 580, high-pressure working fluid can be sent into the second pressure regulating chamber 562. On the other hand, a second valve 581 is disposed between the second pressure adjustment chamber 562 and the third pressure adjustment chamber 563. Similar to the first valve 580, the second valve 581 can be controlled to open and close by a plunger type solenoid constituted by a coil 571, an iron core 574, an elastic body 585 (spring) and a connecting shaft 577. By opening the second valve 581, the working fluid can be sent from the second pressure adjustment chamber 562 to the third pressure adjustment chamber 563. That is, by controlling the opening and closing of the two (plural) valves 580 and 581, a control pressure between the pressure of the working fluid before expansion and the pressure of the working fluid after expansion is created, and the second pressure It becomes possible to maintain the inside of the adjustment chamber 562 and thus the second pressure chamber 431b of the actuator 406 at the generated control pressure. When the pressure in the second pressure regulating chamber 562 is higher than the desired pressure, the first valve 580 is closed and the second valve 581 is opened. When the pressure is lower than the desired pressure, the first valve 580 is opened and the second valve 581 is opened. The two valve 581 is closed.

  Further, as shown in the block diagram of FIG. 16B, the pressure regulator 500C includes a pressure sensor 590 that detects the pressure in the second pressure adjustment chamber 562, and the valves 580 and 581 based on the detection result of the pressure sensor 590. A controller 591 that controls opening and closing may be provided. The pressure sensor 590 may be disposed in the second pressure chamber 431b of the actuator 406 in the expander 303. The controller 591 acquires a sensor signal from the pressure sensor 590, and calculates the difference between the target pressure value and the current pressure value. When the calculated difference is not within the predetermined allowable range, the opening and closing of the first valve 580 and the second valve 581 are controlled so that the difference becomes small. Specifically, when the current pressure value is smaller than the target pressure value, the solenoid on the first valve 580 side is driven for a certain period of time, and a certain amount of high-pressure working fluid is discharged from the first pressure adjustment chamber 561. It flows into the second pressure adjustment chamber 562. Conversely, when the current pressure value is larger than the target pressure value, the solenoid on the second valve 581 side is driven for a certain period of time, and the working fluid is transferred from the second pressure adjustment chamber 562 to the third pressure adjustment chamber 563. Move.

  By repeatedly performing such processing, the pressure in the second pressure adjusting chamber 562 can be quickly and accurately adjusted to a desired pressure. Since there is no need to constantly flow current through the solenoids (coils 570 and 571) that open and close the first valve 580 and the second valve 581, the power consumption of the pressure regulator 500C can be suppressed, and the recovery efficiency of the expansion energy of the working fluid It is advantageous for improvement. If a program for periodically monitoring the input from the pressure sensor 590 is incorporated in the controller 591, even if a pressure fluctuation occurs due to unavoidable leakage of the working fluid, the second pressure adjustment chamber 562 It is possible to automatically restore the desired pressure to the desired pressure.

(Third embodiment)
As described in the first embodiment, the features of the expander shown in the second embodiment are suitably used for an expander-integrated compressor in which the expander unit and the compressor unit are integrated via a shaft. can do. FIG. 17 is a longitudinal sectional view of such an expander-integrated compressor.

  The expander-integrated compressor 700 includes a hermetic container 11, a scroll-type compressor unit 20 disposed on the upper side of the hermetic container 11, and a two-stage rotary type disposed on the lower side of the hermetic container 11. The expander section 400, the rotary motor 12 disposed between the compressor section 20 and the expander section 400, and the shaft 13 shared by the compressor section 20, the expander section 400, and the rotary motor 12. I have. When the rotary motor 12 rotates the shaft 13, the compressor unit 20 operates. In the expander-integrated compressor 700, the rotational force applied to the shaft 13 when the working fluid (refrigerant) expands in the expander unit 400 is used as auxiliary power for the compressor unit 20. Since the expansion energy of the working fluid is directly transmitted to the compressor unit 20 without once being converted into electric energy, high energy recovery efficiency can be expected.

  As described in the second embodiment, the expander unit 400 includes the port member 412b provided with the second suction hole 412c for changing the suction volume, and the actuator 406 for rotationally displacing the port member 412b. I have. The structures and functions of the port member 412b and the actuator 406 are as described in the second embodiment.

  Further, the basic structure and operation principle of the compressor unit 20 and the expander unit 400 are also as described in the first embodiment.

  According to the expander-integrated compressor 700 of FIG. 17, the actuator 406 is driven by the pressure difference between the working fluid provided by the control pressure pipe 435 and the working fluid provided by the suction pipe 53, and the position (center of the port member 412b) The rotation angle around the axis O can be changed. By controlling the position of the port member 412b, the suction volume of the expander unit 400 can be freely controlled. According to such a heat pump using the expander-integrated compressor 700, the flow rate of the working fluid flowing through the expander unit 400 can be freely controlled without providing a bypass circuit, and thus a highly efficient heat pump. The system can be realized.

(Fourth embodiment)
The actuator incorporated in the expander of the second embodiment can be suitably employed in the expander or the expander-integrated compressor, but can be configured as a rotary actuator for another application.

  FIG. 18 is a longitudinal sectional view of a rotary actuator according to the fourth embodiment. 19 is a cross-sectional view taken along the line D5-D5 of FIG. As shown in FIGS. 18 and 19, the rotary actuator 800 includes a cylinder 806, a shaft 801 that passes through the inside and outside of the cylinder 806, a piston 807 that rotates eccentrically in the cylinder 806 and rotates the shaft 801, and the cylinder 806 and the piston And a vane 812 that partitions the pressure chamber 808 formed between the first pressure chamber 808a and the second pressure chamber 808b.

  The shaft 801 has an eccentric portion 802 that bulges outward in the radial direction at an intermediate portion thereof, and has one end passing through the upper end plate 803 and the other end passing through the lower end plate 804. A closing member 805 is disposed below the lower end plate 804. The upper end plate 803 and / or the closure member 805 may include a bearing for the shaft 801. The eccentric portion 802 of the shaft 801 is disposed inside the cylinder 806 and is fitted with a ring-shaped piston 807.

  The rotary actuator 800 includes a vane 812, a spring 809, a suction pipe 810, and a control pressure pipe 811. The vane 812 is reciprocally held in a vane groove provided in the cylinder 806 so that the tip is in contact with the piston 807. The spring 809 biases the vane 812 toward the piston 807. A first inflow hole 820 connected to the first pressure chamber 808a and a second inflow hole 821 connected to the second pressure chamber 808b are formed in the upper end plate 803 that covers the upper side of the cylinder 806. A suction pipe 810 is connected to the first pressure chamber 808a via a first inflow hole 820. A control pressure pipe 811 is connected to the second pressure chamber 808b via a second inflow hole 821. A force is applied to the piston 807 due to a pressure difference between the first fluid flowing into the first pressure chamber 808a and the second fluid flowing into the second pressure chamber 808b, and the eccentric portion 802, and thus the entire shaft 801, rotates. A first stop 813a and a second stop 813b are formed on the inner peripheral surface of the cylinder 806 at a predetermined angle in the circumferential direction. These stops 813a and 813b limit the rotation range when the piston 807 rotates due to the pressure difference of the working fluid.

  In this embodiment, an elastic body that gives a repulsive force to the rotation of the shaft 801 is not provided, but an elastic body (rotation spring 439: see FIG. 12B) as described in the second embodiment may be provided. Good. By doing so, it is possible to control the rotation angle of the shaft 801 by adjusting the differential pressure between the first fluid that flows into the first pressure chamber 808a and the second fluid that flows into the second pressure chamber 808b. It becomes. Note that the first fluid and the second fluid may be the same type of fluid or different types of fluid. As such a fluid, for example, oil in a hydraulic circuit, refrigerant in a refrigerant circuit, or air in a pneumatic circuit can be used.

  As described above, the expander of the present invention provides an efficient means for recovering the expansion energy of the working fluid in the refrigeration cycle, and in particular, achieves high efficiency of the heat pump using the expander-integrated compressor. , Has great utility value.

  The present invention relates to an expander applied to a refrigeration cycle apparatus (heat pump), and further to a heat pump using the expander.

  There has been proposed a power recovery type refrigeration cycle in which expansion energy of a working fluid (refrigerant) is recovered by an expander, and the recovered energy is used as part of the work of the compressor. As such a refrigeration cycle, for example, a refrigeration cycle using a fluid machine in which an expander and a compressor are connected by a shaft (hereinafter referred to as an “expander-integrated compressor”) is known (Japanese Patent Laid-Open No. 2001-2001). 116371).

  Hereinafter, a refrigeration cycle using an expander-integrated compressor will be described.

  FIG. 20 shows a refrigeration cycle using a conventional expander-integrated compressor. In this refrigeration cycle, the compressor 1, the gas cooler (heat radiator) 2, the expander 3 and the evaporator 4 constitute a main circuit 8 of working fluid (refrigerant). The compressor 1, the expander 3, and the rotary motor 6 Is connected to the shaft 7 to form an expander-integrated compressor. The refrigerant circuit includes a sub circuit 9 together with the main circuit 8. The sub circuit 9 branches from the main circuit 8 on the outlet side of the gas cooler 2, and merges with the main circuit 8 on the inlet side of the evaporator 4. The working fluid passing through the main circuit 8 is expanded in the expander 3, and the working fluid passing through the sub circuit 9 is expanded by the expansion valve 5.

  The working fluid is compressed from a low temperature and a low pressure to a high temperature and a high pressure in the compressor 1 and then cooled to a low temperature and a high pressure in the gas cooler 2. And after expanding to low temperature low pressure (gas-liquid two phases) in the expander 3 or the expansion valve 5, it is heated by the evaporator 4 and returns to low temperature low pressure (gas phase). The expander 3 collects expansion energy of the working fluid and converts it into rotational energy of the shaft 7. This rotational energy is used as a part of work for driving the compressor 1, and as a result, the power of the rotary motor 6 can be reduced.

  Here, the operation of the refrigeration cycle when the expansion valve 5 is fully closed and the mass flow rate of the working fluid in the sub circuit 9 is zero will be described.

  If the suction volume of the compressor 1 is Vcs, the suction volume of the expander 3 is Ves, and the rotational speed of the shaft 7 is N, the volume flow rate of the working fluid on the inlet side of the compressor 1 and the inlet side of the expander 3 The volume flow rates of the working fluid are (Vcs × N) and (Ves × N), respectively. Since the mass flow rate of the working fluid in the sub circuit 9 is zero, the mass flow rate in the compressor 1 and the mass flow rate in the expander 3 are equal. Assuming that this mass flow rate is G, the density of the working fluid on the inlet side of the compressor 1 and the density of the working fluid on the inlet side of the expander 3 can be calculated from the ratio of the respective volume flow rate and mass flow rate {G / ( Vcs × N)}, {G / (Ves × N)}. From these equations, the ratio of the density of the working fluid on the inlet side of the compressor 1 and the density of the working fluid on the inlet side of the expander 3 is {G / (Vcs × N)} / {G / (Ves × N )}, That is, (Ves / Vcs) and becomes constant.

FIG. 21 shows a Mollier diagram of the refrigeration cycle. In the figure, the compression process in the compressor 1 corresponds to AB, the heat release process in the gas cooler 2 corresponds to BC, the expansion process in the expander 3 corresponds to CD, and the evaporation process in the evaporator 4 corresponds to DA. Since the density ratio of the working fluid at the point A on the inlet side of the compressor 1 and the point C on the inlet side of the expander 3 is constant at (Ves / Vcs), the density of the working fluid at the point A is ρ _0. Then, the density ρ _c at the point C is (Vcs / Ves) ρ ₀ . Assuming that the density of the point A is constant, when the pressure at the point C is increased, it changes from the point C to the point C ′ on the line ρ _c = (Vcs / Ves) ρ _0. Become. That is, it becomes impossible to change the point C to the point C ″ increased by the pressure along the isotherm (T = T _c ), and the free control of the refrigeration cycle is impeded. Since there is an optimum high pressure at which the coefficient of performance (COP) is maximum at the heat source temperature (for example, Japanese Patent Application Laid-Open No. 2002-81766), efficient operation cannot be performed unless the temperature and pressure are freely controlled.

  The restriction that the ratio of the density on the inlet side of the compressor 1 and the density on the inlet side of the expander 3 is constant is that the mass flow rate in the compressor 1 and the mass flow rate in the expander 3 are equal, and the ratio of the volume flow rate. Is due to the constant. This restriction can be avoided by opening the expansion valve 5 and allowing a part of the working fluid flowing through the refrigerant circuit to flow through the sub circuit 9 (Japanese Patent Laid-Open No. 2001-116371).

  In a power recovery type heat pump using a conventional expander-integrated compressor, in order to avoid the restriction of a constant density ratio caused by the compressor and the expander having the same rotation speed, the working fluid is supplied to the expander. Along with the main circuit provided with the sub-circuit provided with the expansion valve. However, this cannot recover the expansion energy of the working fluid that passes through the subcircuit.

  The problem that the expansion energy of the working fluid cannot be efficiently recovered becomes prominent when an expander-integrated compressor is used, but also occurs when a separate expander that is not connected to the compressor by a shaft is used. . When a separation type expander is used, the expansion energy of the working fluid is recovered by a generator connected to the expander. Since the power generation efficiency of the generator decreases as it goes away from the rated speed, it is desirable that the generator be operated near the rated speed. However, in the refrigeration cycle, since the circulating amount and density of the working fluid change according to the operating conditions, it is difficult to operate the generator only near the rated speed. For this reason, even in the separation type expander, it is not easy to efficiently recover the expansion energy of the working fluid.

  This invention is made | formed in view of said situation, and it aims at providing the expander which can collect | recover the expansion energy of a working fluid efficiently. It is another object of the present invention to provide a heat pump including the expander.

That is, the present invention
A cylinder,
A shaft having an eccentric part;
A piston that fits into the eccentric part and rotates eccentrically inside the cylinder;
N rotary expansion mechanisms (n is an integer of 2 or more) having a partition member for partitioning the space between the cylinder and the piston into a suction side space and a discharge side space;
A first suction hole for sucking the working fluid into the suction side space of the first expansion mechanism;
a communication hole that connects the discharge side space of the kth expansion mechanism (k is an integer from 1 to n-1) and the suction side space of the (k + 1) th expansion mechanism to form one space;
a discharge hole for discharging the working fluid from the discharge side space of the nth expansion mechanism;
A connection position with the suction side space of the first expansion mechanism is variable, and a second suction hole for sucking the working fluid into the suction side space;
An expander is provided.

  The present invention also provides an expander-integrated compressor comprising an expander unit comprising the expander according to the present invention and a compressor unit integrally connected to the expander unit via the shaft. To do.

  Furthermore, the present invention provides a heat pump comprising the expander or the expander-integrated fluid machine according to the present invention.

  In the expander of the present invention, the timing of transition from the working fluid suction process to the working fluid expansion process is adjusted by changing the connection position between the suction side space of the first expansion mechanism and the second suction hole. The ratio of the length of time during which the expansion process is performed to the length of time during which the inhalation process is performed can be controlled. For this reason, according to the present invention, it is possible to change the above (Ves / Vcs). For example, in a refrigeration cycle using an expander-integrated compressor, it is possible to avoid the restriction of a constant density ratio. Therefore, it is possible to efficiently recover the expansion energy of the working fluid by supplying the entire amount of the working fluid to the expander without providing the subcircuit of the working fluid.

  When the expander of the present invention is used as a separation type expander, the rotation speed of the expander can be controlled while maintaining the amount of working fluid flowing into the expander. For this reason, it becomes easy to make the rotation speed of the generator connected to the expander near the rated rotation speed, and to maintain the power generation efficiency by the generator high.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
1 is a longitudinal sectional view showing a configuration of an expander-integrated compressor according to a first embodiment of the present invention, and FIG. 2A is a cross-sectional view taken along a line D1-D1 of an expander portion of the expander-integrated compressor of FIG. 2B is a cross-sectional view taken along the D2-D2 cross section of the expander unit, FIG. 3A is a partially cutaway perspective view of a fixing portion of an upper end plate of the expander unit, and FIG. 3B is an upper end of the expander unit. FIG. 3C is a partially cutaway perspective view showing a state in which the fixed portion and the movable portion of the upper end plate are integrated.

  The expander-integrated compressor 100 according to this embodiment includes a hermetic container 11, a scroll-type compressor unit 20 disposed on the upper side, and a two-stage rotary type expander unit disposed on the lower side. 40, and the rotary motor 12 including the rotor 12a and the stator 12b disposed between the compressor unit 20 and the expander unit 40 are connected to the compressor unit 20, the expander unit 40, and the rotary motor 12. And a shaft 13. The shaft 13 may be formed by connecting a plurality of portions to one axis.

  The scroll-type compressor unit 20 includes a fixed scroll 21, an orbiting scroll 22, an Oldham ring 23, a bearing member 24, a muffler 25, a suction pipe 26, and a discharge pipe 27. The orbiting scroll 22 fitted to the eccentric shaft 13a of the shaft 13 and restrained by the Oldham ring 23 is rotated with the spiral wrap 22a meshing with the wrap 21a of the fixed scroll 21. Accordingly, the crescent-shaped working chamber 28 formed between the wraps 21a and 22a is reduced in volume while moving from the outside to the inside, thereby compressing the working fluid sucked from the suction pipe 26. . The compressed working fluid passes through a discharge hole 21b provided in the central portion of the fixed scroll 21, an inner space 25a of the muffler 25, and a flow path 29 penetrating the fixed scroll 21 and the bearing member 24 in this order, and is in a sealed container. 11 is discharged into the internal space 11a. The working fluid discharged to the inner space 11a is discharged from the discharge pipe 27 to the refrigeration cycle after the mixed lubricating oil is separated by gravity, centrifugal force, or the like while it stays in the inner space 11a.

  The two-stage rotary expander unit 40 includes a first cylinder 41, a second cylinder 42 that is thicker than the first cylinder 41, and an intermediate plate 43 that partitions the cylinders 41 and 42. The first cylinder 41 and the second cylinder 42 are arranged concentrically with each other. The expander unit 40 is further fitted to the eccentric portion 13 b of the shaft 13, and is held in a reciprocating manner in a first piston 44 that rotates eccentrically in the first cylinder 41 and a vane groove of the first cylinder 41. A first vane 46 with one end contacting the first piston 44, a first spring 48 contacting the other end of the first vane 46 and urging the first vane 46 toward the first piston 44; The second cylinder 42 is fitted to the eccentric portion 13c of the shaft 13, and is held in a reciprocating manner in a second piston 45 that rotates eccentrically in the second cylinder 42 and a vane groove of the second cylinder 42. A second vane 47 whose end is in contact with the second piston 45, and a second spring 49 which is in contact with the other end of the second vane 47 and biases the second vane 47 toward the second piston 45. ing.

  The first cylinder 41, the shaft 13, the first piston 44, and the first vane 46 constitute a first (first stage) expansion mechanism. Similarly, the second cylinder 42, the shaft 13, the second piston 45, and the second vane 47 constitute a second (second stage) expansion mechanism. The pistons 44 and 45 and the vanes 46 and 47 may be integrated (a so-called swing piston).

  The expander unit 40 further includes an upper end plate 73 and a lower end plate 51 disposed so as to sandwich the first and second cylinders 41 and 42 and the intermediate plate 43. The upper end plate 73 and the middle plate 43 sandwich the first cylinder 41 from above and below, and the middle plate 43 and the lower end plate 51 sandwich the second cylinder 42 from above and below. By holding the upper end plate 73, the middle plate 43 and the lower end plate 51, a working chamber whose volume changes in accordance with the rotation of the pistons 44 and 45 is formed in the first cylinder 41 and the second cylinder 42. The The upper end plate 73 and the lower end plate 51 are blocking members that close the cylinders 41 and 42, and also function as bearing members that rotatably hold the shaft 13 together with the bearing member 24 of the compressor unit 20. Similarly to the compressor unit 20, the expander unit 40 also includes a muffler 52, a suction pipe 53, and a discharge pipe 54.

  As shown in FIGS. 2A and 2B, inside the first cylinder 41, a suction side working chamber 55a (first suction side space) partitioned by a first piston 44 and a first vane 46 and a discharge side are provided. The working chamber 55b (first discharge side space) is disposed inside the second cylinder 42 by the second piston 45 and the second vane 47, and the suction side working chamber 56a (second suction side space) and the discharge. Side working chambers 56b (second discharge side spaces) are respectively formed. The total volume of the two working chambers 56 a and 56 b in the second cylinder 42 is larger than the total volume of the two working chambers 55 a and 55 b in the first cylinder 41. The discharge-side working chamber 55b of the first cylinder 41 and the suction-side working chamber 56a of the second cylinder 42 communicate with each other through a communication hole 43a provided in the intermediate plate 43, and one working chamber (expansion chamber) ). The high-pressure working fluid flows into the working chamber 55a and then expands to a low pressure while rotating the shaft 13 in the working chamber formed by the working chamber 55b and the working chamber 56a.

  As shown in FIG. 1, the upper end plate 73 includes a fixed portion 71 and a movable portion 72. As shown in FIG. 3A, the fixed portion 71 has a through hole 71 f for fitting the movable portion 72 together. The through-hole 71f has a cylindrical concave surface 71a, a cylindrical concave surface 71b having the same central axis 70 as the cylindrical concave surface 71a and having an inner diameter smaller than the cylindrical concave surface 71a, and a step surface 71c connecting the cylindrical concave surfaces 71a and 71b. being surrounded. When the fluid machine (expander-integrated compressor 100) is assembled, the central axis 70 coincides with the central axis of the shaft 13.

  Inside the fixed portion 71, as an inflow path for guiding the working fluid from the suction pipe 53 to the working chamber 55a, an inflow path 71d (first inflow path) and an inflow path 71e (first flow path) that is a branch path from the inflow path 71d. 2 inflow passages). As shown in FIGS. 1 and 2A, the first cylinder 41 is provided with an inflow path 41a and a first suction hole 41b as a flow path communicating with the inflow path 71e. One cylinder 41 communicates with a working chamber 55a on the suction side.

  As shown in FIG. 3B, the movable portion 72 of the upper end plate 73 has a through hole 72a for rotatably holding the shaft 13, and has a cylindrical convex surface that abuts on the cylindrical concave surface 71a of the fixed portion 71 as an outer peripheral surface. 72b, a cylindrical convex surface 72c that contacts the cylindrical concave surface 71b of the fixed portion 71, and a step surface 72g that contacts the step surface 71c of the fixed portion 71 between the cylindrical convex surfaces 72b and 72c. The cylindrical convex surface 72c of the movable portion 72 of the upper end plate 73 is provided with a gear 72e that goes around the cylindrical convex surface 72c in the circumferential direction. The movable portion 72 further includes a flow path groove 72d that circulates along the circumferential direction on the cylindrical convex surface 72b, and a second suction hole 72f connected to the flow path groove 72d. As shown in FIGS. 1 and 2A, the second suction hole 72f extends in the axial direction from the flow path groove 72d toward the working chamber 55a of the first cylinder 41, and the working chamber 55a on the suction side in the first cylinder 41. Communicating with

  As shown in FIG. 3C, the fixed portion 71 and the movable portion 72 are integrated by rotatably fitting the movable portion 71 into the through hole 71 f of the fixed portion 71. The stepped surface 71c of the fixed part 71 and the stepped surface 72g of the movable part 72 are in contact with each other to prevent the movable part 72 from slipping out above the fixed part 71. The lower end surface of the fixed portion 71 and the lower end surface of the movable portion 72 constitute the same plane, and this plane constitutes a partition above the first cylinder 41.

  When the movable portion 72 is rotated, the second suction hole 72f rotates and moves around the central axis 70 while maintaining a constant distance from the central axis 70 of the shaft 13. The rotation of the movable portion 72 causes a relative change in the position of the second suction hole 72 in the working chamber 55a on the suction side of the first cylinder 41. That is, while the connection position between the first suction hole 41b and the working chamber 55a on the suction side of the first cylinder 41 is fixed, the connection position between the second suction hole 72f and the working chamber 55a is variable. As will be described later, the change in the connection position of the second suction hole 72f makes it possible to avoid the restriction of a constant density ratio in the expander-integrated compressor.

  As described with reference to FIGS. 3A, 3B, and 3C, the second suction hole 72f is a blocking member that blocks the end surface of the first cylinder 41 included in the first fluid mechanism into which the working fluid first flows. The end plate 73 may be provided. This is because the movable second suction hole 72f can be configured with a simple configuration. Moreover, since the cylinder 41 side of the upper end plate 73 is a flat surface, it is easy to increase the processing accuracy even if the end plate 73 is constituted by a plurality of parts.

  In addition, as described above, it is preferable that at least a part of the end plate 73 is the movable portion 72 that can rotate around the shaft 13 and the second suction hole 72 f is provided in the movable portion 72. This is because it is easy to ensure a large movement range of the second suction hole 72f.

  Further, in the present embodiment, the movable portion 72 includes a cylindrical bearing surface that supports the shaft 13 (the inner peripheral surface of the through hole 72a). Therefore, it is not necessary to separately provide a bearing for supporting the shaft 13, thereby suppressing an increase in the number of parts.

  The fixed portion 71 has an annular shape, and an inflow passage 71d (first inflow passage) that supplies the working fluid from the outside of the expander portion 40 to the second suction hole 72f provided in the movable portion 72. An inflow path 71e (second inflow path) that branches from the inflow path 71d and supplies the working fluid to the first suction hole 41b is provided inside. The movable portion 72 is rotatably joined to such a fixed portion 71. Providing the two inflow passages 71d and 71e inside the fixed portion 71 eliminates the need for piping for guiding the working fluid to the second suction hole 72f, which is advantageous for space saving inside the sealed container 11. In addition, since the inflow passages 71d and 71e are provided in the fixed portion 71, the problem of leakage of the working fluid hardly occurs.

  Returning to FIG. 1, the description will be continued. The fixed portion 71 of the upper end plate 73 is further provided with a gear 75 that meshes with the gear 72 e of the rotating portion 72 and a rotary electric motor 76 (electric actuator) that drives the gear 75. The movable portion 72 is driven by a rotary electric motor 76 via gears 72e and 75. Thus, the expander unit 40 may further include drive mechanisms 75 and 76 that rotate the movable unit 72. The drive mechanisms 75 and 76 are connected to a controller (not shown) that is provided outside the sealed container 11 and controls the rotation angle of the movable part 72, and receives the control signal from the controller to move the movable part 72. Rotate to control the connection position to the working chamber 55a. If a stepping motor or a servo motor is used as the rotary electric motor 76, the position of the second suction hole 72f can be controlled with high accuracy. Further, a detector (for example, an encoder) that detects the rotation angle of the movable portion 72 may be provided. In addition, as a drive means of the movable part 72, means other than the rotary electric motor 76, for example, an actuator using a pressure difference of fluid may be used.

  The working fluid that has flowed into the expander section 40 from the suction pipe 53 is divided into two paths from the inflow path 71d of the fixing section 71 of the upper end plate 73 and flows into the working chamber 55a. The first path is a path that passes through the inflow path 71d in the fixed portion 71, the branch inflow path 71e, the inflow path 41a in the first cylinder 41, and the first suction hole 41b. The second path is a path that passes through the inflow path 71d in the fixed part 71, the flow path groove 72d of the movable part 72, and the second suction hole 72f. As described above, in the expander unit 40, the connection position between the first suction hole 41b in which the connection position with the working chamber 55a is fixed from the intake pipe 53 to the first working chamber 55a and the working chamber 55a are variable. The working fluid is supplied via the second suction hole 72f. In these two paths, there is no need to arrange a flow rate control mechanism such as an electromagnetic valve or a differential pressure valve that can be opened and closed.

  The working fluid sucked into the first cylinder 41 passes through the second cylinder 42, passes through the discharge hole 51 a provided in the lower end plate 51, the inner space 52 a of the muffler 52, and the first and second cylinders 41 and 42. It discharges from the discharge pipe 54 to the refrigerating cycle via the flow path 57 which penetrates in this order. The discharge hole 51a may be provided in the second cylinder 42.

  As shown in FIG. 2B, a discharge valve 74 is installed in the discharge hole 51 a provided in the lower end plate 51. The discharge valve 74 is made of, for example, a metal thin plate, and is disposed so as to close the discharge hole 51 a from the inner space 52 a side of the muffler 52. The discharge valve 74 is a differential pressure valve that opens when the pressure on the upstream side (the working chamber 56b side on the discharge side of the second cylinder 42) becomes higher than the pressure on the downstream side (the inner space 52a side of the muffler 52). The discharge valve 74 has a function of preventing overexpansion of the working fluid in the expander unit 40.

  4A, 4B, and 4C show the positions of the first suction hole 41b and the second suction hole 72f. The position of the second suction hole 72f is indicated by an angle φ with reference to the position of the first vane 46 around the shaft 13, and is 20 ° (FIG. 4A), 90 ° (FIG. 4B), 180 ° (FIG. 4C), respectively. More precisely, the angle φ is a rotational direction of the shaft 13 about the center axis 70 (illustrated) with respect to the first straight line 80 connecting the contact point between the first vane 46 and the first piston 44 and the center axis 70 of the shaft 13. (Clockwise in this example) is an angle when rotating to the second straight line 90 connecting the second suction hole 72f and the central axis 70 of the shaft 13. According to this notation method, in the illustrated example, the first suction hole 41b is fixed at a position of 20 °. Further, the discharge hole 51a is fixed at a position of 340 ° in the same notation in the second cylinder. On the other hand, the position of the second suction hole 72f can be arbitrarily set between 0 ° and 360 °.

  FIG. 5A shows an operation principle diagram of the first cylinder 41 when the angle φ of the second suction hole 72f is 90 °, and FIG. 5B shows an operation principle diagram of the second cylinder 42 corresponding to the above. Here, the rotation angle θ of the shaft 13 is set to 0 ° when the contact point between the first cylinder 41 and the first piston 44 is at a so-called top dead center located in the first vane 46, and in the rotation direction of the shaft 13. A certain clockwise direction is displayed as positive.

  The working fluid flows into the working chamber 55a generated after θ = 0 ° from the first suction hole 41b after θ = 20 °. After θ = 90 °, the working fluid flows into the working chamber 55a from the first suction hole 41b and the second suction hole 72f. After θ = 360 °, the working chamber 55a changes to the working chamber 55b and communicates with the working chamber 56a of the second cylinder 42 through the communication hole 43a. When the shaft 13 further rotates, at θ = 380 ° (not shown), the contact point between the first cylinder 41 and the first piston 44 passes through the first suction hole 41b, and the working chamber 55b, the first suction hole 41b, Is disconnected. In the conventional two-stage rotary expander unit, the working fluid suction process ends at this point.

  On the other hand, since the second suction hole 72f is provided in the expander unit 40 of the present embodiment, the inflow of the working fluid from the second suction hole 72f continues even when θ = 380 °. In this expander section 40, θ = 450 °, and the contact between the first cylinder 41 and the first piston 44 passes through the second suction hole 72f, and the communication between the working chamber 55b and the second suction hole 72f is cut off. At that time, the working fluid suction process ends.

  When the suction process is completed, the working fluid expansion process is started. When the shaft 13 further rotates, the volume of the working chamber 55b decreases. However, since the second cylinder 42 is higher in the axial direction and has a larger volume than the first cylinder 41, the volume of the working chamber 56a is larger than that. To increase. As a result, as the shaft 13 rotates, the sum of the volumes of the working chamber 55b and the working chamber 56a increases, and the working fluid expands. When θ = 700 ° (not shown), the contact between the second cylinder 42 and the second piston 45 passes through the discharge hole 51a, and the working chamber 56a communicates with the discharge hole 51a. At this point, the expansion process ends.

  When the expansion process is finished, the discharge process of the working fluid is started. At θ = 720 °, the working chamber 55b disappears, the working chamber 56a changes to the working chamber 56b, and further, as the shaft 13 rotates, the volume of the working chamber 56b decreases and the working fluid is discharged from the discharge hole 51a. . When θ = 1080 °, the working chamber 56b disappears, and the discharge process ends.

  FIG. 6A shows the relationship between the rotation angle θ of the shaft 13 and the transition point of each process from suction to discharge when the angle φ of the second suction hole 72f is 20 °, 90 °, and 180 °. As is clear from the above description, the rotation angle θ of the shaft 13 at which the suction process ends is an angle when the contact point between the first cylinder 41 and the first piston 44 passes through the second suction hole 72f for the second time. . This angle can be expressed as θ = (360 + φ). Therefore, as the angle φ of the second suction hole 72f increases, the timing of transition from the suction process to the expansion process is delayed, the suction process is lengthened, and the expansion process is shortened. That is, the ratio of the length of time during which the expansion process is performed to the length of time during which the inhalation process is performed becomes small.

  FIG. 6B shows the relationship between the rotation angle θ of the shaft 13 and the working chamber volume. The working fluid moves in the order of the working chamber 55a, the working chamber 55b, the working chamber 56a, and the working chamber 56b. In this process, the volume of the working chamber changes in a sinusoidal curve. On the vertical axis in the figure, the suction volume Vesφ that is the volume of the working chamber at the end of the suction process when the angle φ of the second suction hole 72f is 20 °, 90 °, and 180 °, and the working chamber at the start of the discharge process The discharge volume Ved which is the volume of is shown. The suction volume Vesφ increases as φ increases, but the discharge volume Ved is constant regardless of φ.

  As described above, in this embodiment, in addition to the fixed first suction hole 41b provided in the conventional two-stage rotary expander unit 40, the movable second suction hole 72f is provided, The suction volume Vesφ that is the volume at the end of the suction process of the working chambers 55a, 55b, 56a, and 56b was made variable. Thereby, the density ratio (Vcs / Vesφ) of the working fluid on the inlet side of the compressor unit 20 and the expander unit 40 can be controlled.

  In FIG. 7, the Mollier diagram of the refrigerating cycle using the expander integrated compressor of this embodiment is illustrated. Since the density ratio can be changed, only the pressure is changed along the isotherm (T = 35 ° C. in the illustrated example) at the point C corresponding to the state on the inlet side of the two-stage rotary expander unit 40. Thus, the temperature and pressure on the inlet side of the two-stage rotary expander unit 40 can be freely controlled, and the conventional expander can be moved to the point C ′ or the point C ″. An efficient refrigeration cycle operation, which was impossible with a refrigeration cycle using a body compressor, is possible.

  In particular, as in the present embodiment, when the second suction hole 72f is formed in the movable portion 72 that can rotate around the axis of the shaft 13, and the angle φ can be adjusted from 0 ° to 360 °, the control is performed. Since the width is large, it is easy to improve the efficiency of the refrigeration cycle.

  Next, the effect obtained by providing the discharge valve 74 in the discharge hole 51a will be described. FIG. 8 shows the relationship between the volume of the working chamber and the pressure (PV diagram). The subscript φ of the symbol in the figure is the angle φ of the second suction hole 72f. Point Pφ represents the start of the expansion process, point Sφ represents the end of the expansion process, and point T represents the start of the discharge process. Since a refrigeration cycle using carbon dioxide as a working fluid is assumed, the inflection point Qφ due to the phase change is shown during the expansion process.

Since the discharge volume Ved is constant, the volume ratio (= Ved / Vesφ) before and after the expansion process decreases as the suction volume Vesφ increases with the movement of the second suction hole 72f, and the pressure at the end of the expansion process Sφ increases. Therefore, for example, when the range of the angle φ of the second suction hole 72f is controlled in the range of 20 ° to 180 °, the pressure S ₁₈₀ at the end of the expansion process when the maximum angle 180 ° is selected is the low pressure of the refrigeration cycle. It is desirable to set the pressure so as to be lower than the side pressure Ped so that underexpansion does not occur. This is because when the underexpansion occurs, a part of energy due to the pressure difference of the working fluid cannot be recovered.

  With this design, overexpansion occurs at least when the angle φ is set to 180 ° or less. Overexpansion is a phenomenon in which the pressure Pedφ is lower than the low pressure side pressure Ped of the refrigeration cycle. When the overexpansion occurs, an overexpansion loss is generated in the discharge process because the working fluid is pushed out from the discharge hole 51a into the inner space 52a of the muffler 52 having a pressure higher than that in the working chamber 56b. The magnitude of the overexpansion loss can be indicated by the area of the triangle RφSφT in FIG.

  However, if the discharge valve 74 is provided in the discharge hole 51a, if overexpansion CφDφ occurs in the working chamber 56b, recompression is performed in the discharge process. In the discharging process, the working chamber 56b becomes smaller in volume as the shaft 13 rotates. If the discharge valve 74 is disposed in the discharge hole 51a, the discharge valve 74 is not opened until the pressure in the working chamber 56b, which has been reduced due to overexpansion, becomes equal to the low-pressure side pressure Pd of the refrigeration cycle. Will be recompressed. Thus, if the discharge valve 74 is arranged, an overexpansion loss can be prevented.

  Hereinafter, other features of the expander-integrated compressor of the present embodiment will be described.

  In the present embodiment, it is preferable that the movable portion 72 of the upper end plate 73 provided with the second suction hole 72f is rotatable about the shaft 13 in the same direction as the rotation direction of the shaft 13. This is because the movable portion 72 can be rotated with a small amount of power by the frictional force between the shaft 13 and the movable portion 72. According to this, it becomes easy to reduce the size of the rotary electric motor 76 and store it in the sealed container 11.

  In this embodiment, if the movable part 72 rotates 360 degrees, it returns to the original position. For this reason, the movable part 72 has only to be rotated in the same direction at all times, and the control of the rotary motor 76 is simple. The frictional force between the shaft 13 and the movable part 72 does not hinder the rotational drive.

  In this embodiment, since the suction volume Vesφ of the expander unit 40 is variable, the compressor unit 20 has a normal structure used for a refrigeration cycle that does not use an expander. About the compressor part 20, since a normal structure can be used as it is, development cost can be reduced.

  When the expander-integrated compressor of the present embodiment is used, the expander unit 40 rotates at the same rotational speed as the compressor unit 20 while controlling the circulation amount of the working fluid in the refrigeration cycle by the rotational speed of the compressor unit 20. The suction volume Vesφ can be adjusted according to the operating conditions. Therefore, it is possible to share the role of the compressor unit 20 and the expander unit 40 in controlling the refrigeration cycle, and the control algorithm of the refrigeration cycle using the expander-integrated compressor is facilitated.

  Although there is no restriction | limiting in the kind of working fluid used for the expander integrated compressor of this embodiment, Carbon dioxide is suitable. This is because the effect of power recovery by the expander becomes more prominent. For this reason, when the working fluid is carbon dioxide, the effect of increasing the efficiency by avoiding the constant density ratio becomes remarkable.

  In the present embodiment, the second suction holes 72f that are movable together with the first suction holes 41b are provided. However, the number of movable suction holes may be two or more, and in this case, the most downstream position is provided. The suction volume Vesφ is determined by the suction hole arranged at the bottom. Further, in this embodiment, the expander unit 40 has two stages, but even when there are three or more stages, the same effect as described above can be obtained by providing the second suction hole that can move with respect to the first-stage cylinder. Can be obtained.

  Next, FIG. 9A shows a configuration of a power recovery type heat pump using the expander-integrated compressor of the present embodiment. The heat pump shown in FIG. 9A includes an expander-integrated compressor 100, a gas cooler (heat radiator) 2, an evaporator 4, and a pipe 88 (refrigerant pipe) that connects them to each other. In the conventional example shown in FIG. 20, the sub-circuit 9 connected in parallel to the expander 3 is indispensable. However, in the heat pump using the expander-integrated compressor of this embodiment, such a sub-circuit is essentially included. Is unnecessary. However, a sub-circuit may be provided for other purposes, for example, for the purpose of stably starting and stopping the heat pump.

  Furthermore, the expander unit 40 of the present embodiment may be used alone, that is, as an expander separated from the compressor. FIG. 9B shows a configuration of a power recovery type heat pump using a separation type expander. This apparatus includes a compressor 81, a gas cooler (heat radiator) 82, an expander 83, and an evaporator 84. Further, the compressor 81, the gas cooler 82, the expander 83, and the evaporator 84 are connected in this order, and the working fluid circulates. A pipe body 88 (refrigerant pipe) is provided. The expander 83 includes the expander unit 40 described with reference to FIG. In this heat pump, the expansion energy of the working fluid obtained by the expander 83 is converted into electric energy by the generator 86 and used as part of the input of the rotary motor 85 that rotates the compressor 81.

  FIG. 10 shows an efficiency curve of a general generator 86. Since the generator 86 is designed to have the highest power generation efficiency at a predetermined rated rotational speed Nr, the power generation efficiency decreases as the rotational speed goes away from the rated rotational speed. For this reason, it is desirable that the rotational speed of the generator 86 be as close to the rated rotational speed Nr as possible. However, in the refrigeration cycle, since the circulation amount and density of the working fluid change, it is difficult to operate only in the vicinity of the rated rotation speed Nr with an expander having a constant suction volume Ves. If the expander unit 40 of the first embodiment is used as the expander 83, the rotation speed can be controlled to be close to the rated rotation speed Nr by adjusting the suction volume Vesφ.

(Second Embodiment)
As mentioned in the previous embodiment, the position of the second suction hole for changing the suction volume of the expander can also be changed by an actuator that uses the pressure difference of the fluid. According to the actuator using the pressure difference of the fluid, the reliability is high under a severe environment such as high temperature and high pressure. Further, there is an advantage that the working fluid to be expanded by the expander can be used as it is for the power source of the actuator. In the present embodiment, a variable suction volume expander including such an actuator will be described. In the present embodiment, the same reference numerals are used for the same components as those described in the first embodiment.

  FIG. 11 is a longitudinal sectional view of an expander according to the second embodiment. As shown in FIG. 11, the expander 303 is a rotary expander. The expander 303 includes a sealed container 11, a generator 86 arranged in the sealed container 11, and an expander unit 400 connected to the generator 86. The expander unit 400 includes a port member 412b (movable member), a housing 413 that houses the port member 412b, and an actuator 406.

  The port member 412b closes the cylinder 41 (first cylinder) of the first expansion mechanism, and can rotate independently of the shaft 13 with the shaft 13 as a rotation center. The port member 412b is provided with an additional second suction hole 412c. The actuator 406 is a fluid pressure actuator using a pressure difference between fluids as a power source, and applies a rotational force having a magnitude based on the pressure difference between the high pressure fluid and the low pressure fluid to the port member 412b. When the rotation angle of the port member 412b around the central axis O is switched, the position of the second suction hole 412c changes. As a result, in the expander unit 400, the timing of transition from the working fluid suction process to the expansion process changes, and the ratio of the length of time during which the expansion process is performed to the length of time during which the suction process is performed changes.

  The working fluid to be expanded by the expander 303 can be used as the high-pressure fluid and low-pressure fluid that are the power source of the actuator 406. In this way, it is not necessary to separately prepare a fluid for operating the actuator 406. In addition, a strict seal structure that prevents mixing of different fluids is unnecessary. The mechanism for using the working fluid as a power source for the actuator 406 will be clarified by the following description.

  In the present embodiment, the actuator 406, the port member 412b, and the cylinder 41 (first cylinder) of the first expansion mechanism are arranged in this order and concentrically in a direction parallel to the central axis O of the shaft 13. ing. Such an arrangement is advantageous for a small expander 303 because it is possible to suppress the size expansion caused by newly providing the actuator 406 and the port member 412b as much as possible.

Hereinafter, each part of the expander 303 will be described individually.
The generator 86 includes a stator 86b fixed to the side wall of the hermetically sealed container 11 and a rotor 86a disposed inside the stator 86b. The shaft 13 is fixed to the center of the rotor 86a. The shaft 13 extends downward from the rotor 13 a and is shared by the expander unit 400.

  An oil reservoir 405 for storing lubricating oil is formed at the bottom of the sealed container 11. The lower end portion of the shaft 13 is disposed in the oil sump 405. An oil pump (not shown) is formed at the lower end of the shaft 13, and an oil supply passage (not shown) is formed inside and / or the outer periphery of the shaft 13. When the shaft 13 rotates, the lubricating oil in the oil reservoir 405 is pumped up by the oil pump and supplied to the sliding portions of the expander unit 400 through the oil supply passage.

  Since the basic structure of the expander unit 400 and the mechanism for expanding the working fluid are as described in the first embodiment, they are omitted here. Note that an actuator 406 and a port member 412b for changing the position of the second suction hole 412c are disposed between the upper end plate 424 as a bearing member and the first cylinder 41, and the first cylinder 41. This embodiment is different from the first embodiment in that the end face is closed by the port member 412b.

  Hereinafter, the port member 412b and the actuator 406 will be described in detail. The port member 412 b has a substantially disk shape with a hole through which the shaft 13 passes in the center, and is disposed inside the housing 413 whose outer shape substantially coincides with the first cylinder 41. The inner diameter of the housing 413 and the outer diameter of the port member 412b are substantially equal, and the displacement of the port member 412b in the radial direction is restricted by the housing 413. However, the port member 412b can smoothly rotate inside the housing 413. A second suction hole 412c is formed in the port member 412b so as to penetrate vertically in the axial direction at a position not overlapping with the piston 430 of the actuator 406. As the port member 412 b rotates, the second suction hole 412 c moves in the rotation direction of the shaft 13.

  12A is a cross-sectional view of the expander shown in FIG. 11 taken along the line D3-D3. As shown in FIG. 12A, the actuator 406 includes a port member driving eccentric portion 412a, a port member driving piston 430, a port member driving cylinder 432, a port member driving vane 433, a port member driving spring 434, and a suction pipe 53. And a control pressure pipe 435. The shaft 13 is located at the center of the port member driving cylinder 432.

  In the following description, the term “port member driving” is omitted for the sake of brevity regarding each component of the actuator 406.

  As shown in FIG. 12A, the eccentric portion 412 a is eccentric with respect to the shaft 13 and is disposed inside the cylinder 432. The upper side of the cylinder 432 is closed by an upper end plate 424 (see FIG. 11). The piston 430 is fitted into the eccentric portion 412a so as to form a pressure chamber 431 (431a, 431b) between the piston 430 and the cylinder 432. The eccentric portion 412a and the piston 430 rotate (specifically, eccentrically swing) in the cylinder 432 while maintaining an eccentric state with respect to the central axis O of the shaft 13. A through hole through which the shaft 13 passes is formed in the eccentric portion 412a. The eccentric part 412a and the shaft 13 are not joined and can rotate independently of each other.

  The vane 433 is reciprocally held in a vane groove provided in the cylinder 432 so that the tip thereof is in contact with the piston 430. The spring 434 biases the vane 433 toward the piston 430.

  The pressure chambers 431a and 431b formed inside the cylinder 432 are separated by a vane 433 into two spaces of a first pressure chamber 431a and a second pressure chamber 431b. Further, the cylinder 432 is provided with a high pressure side inflow hole 450 and a low pressure side inflow hole 451. The high pressure side inflow hole 450 and the low pressure side inflow hole 451 are separated from each other by a predetermined angle in the circumferential direction, and penetrate through the inside and outside of the cylinder 432. A suction pipe 53 is connected to the first pressure chamber 431a via a high-pressure side inflow hole 450. The suction pipe 53 supplies a high-pressure working fluid before expansion to the first pressure chamber 431a. A control pressure pipe 435 is connected to the second pressure chamber 431b through a low pressure side inflow hole 451. The control pressure pipe 435 supplies a working fluid having a pressure lower than that of the working fluid supplied to the first pressure chamber 431a to the second pressure chamber 431b. The differential pressure between the first pressure chamber 431a and the second pressure chamber 431b gives a rotational force to the piston 430. The piston 430 that receives the rotational force from the differential pressure of the working fluid rotates the eccentric portion 412a and the port member 412b.

  Also, the cylinder 432 passes through the upper end plate 424 from the suction pipe 53, passes through the cylinder 432, the housing 413, and the first cylinder 41 to suck the working fluid into the working chamber 55 a of the first cylinder 41. A suction passage 437 is formed.

  That is, the expander unit 400 in the expander 303 of the present embodiment is connected to the first suction hole 41b formed in the first cylinder 41, and the suction path for sending the working fluid (refrigerant) to the first cylinder 41. 437 and a high-pressure side inflow hole 450 as a branch path branched from the suction path 437. The high-pressure chamber 431a of the actuator 406 and the high-pressure side inflow hole 450 are connected, and the high-pressure working fluid supplied to the actuator 406 through the high-pressure side inflow hole 450 is used as the high-pressure fluid for driving the actuator 406. Further, the actuator 406 and the port member 412b are arranged adjacent to each other so that one end of the second suction hole 412c provided in the port member 412b is connected to the high pressure chamber 431a of the actuator 406, and as a high pressure fluid The working fluid supplied to the actuator 406 is supplied to the working chamber 55a (see FIG. 2A) in the first cylinder 41 through the second suction hole 412c provided in the port member 412b.

  In this way, it is not necessary to separately prepare a fluid for operating the actuator 406. A strict seal structure that prevents mixing of different types of fluids is not necessary, and the problem that the characteristics of the refrigeration cycle change due to mixing of different types of fluids does not occur. Further, by using the working fluid used in the expander 303 as a power source for the actuator 406, it is not necessary to supply energy such as electric power from the outside, which is advantageous in improving the recovery efficiency of the working fluid expansion energy.

  Further, on the inner peripheral surface of the cylinder 432, a first stopper 436a and a second stopper 436b having a convex shape toward the central axis O of the shaft 13 are provided at a predetermined angle in the circumferential direction. These stoppers 436a and 436b have a pressure difference between the piston 430 and the working fluid (when the working fluid (refrigerant) is carbon dioxide, the rated pressure is about 10 MPa on the high pressure side and about 3 to 5 MPa on the low pressure side. ) To limit the movable range (rotation angle around the central axis O) when rotating. As a result, the port member 412b is only allowed to rotate within a range of a predetermined angle (for example, about 180 °).

  Note that the rotation center of the piston 430 of the actuator 406 may coincide with the rotation center of the shaft 13. However, if the structure in which the piston 430 rotates eccentrically as in the present embodiment is adopted, the space for forming the second suction hole 412c penetrating the port member 412b up and down can be secured with a margin, and the expander can be downsized. Is also advantageous.

  12B is a cross-sectional view taken along line D4-D4 of the expander 303 shown in FIG. As shown in FIG. 12B, a rotation spring 439 (biasing means) is attached to the port member 412b. The rotary spring 439 is preferably incorporated in the port member 412b. The rotation spring 439 is interposed between the port member 412b and the housing 413 (or the cylinder 432), and always urges the port member 412b, the eccentric portion 412a, and the piston 430 in a predetermined rotation direction. As shown in FIG. 12A, in the present embodiment, since the first pressure chamber 431a is on the high pressure side and the second pressure chamber 431b is on the low pressure side, the biasing direction of the rotary spring 439 is determined according to the volume of the first pressure chamber 431a. The decreasing direction, that is, the position of the second suction hole 412c approaches the first suction hole 41b (see FIG. 2A). By such an action of the rotary spring 439, the position of the port member 412b can be continuously changed within the movable range determined by the stoppers 436a and 436b. Further, the port member 412b can be rotated in both forward and reverse directions under the relationship that the working fluid supplied to the first pressure chamber 431a is high pressure and the working fluid supplied to the second pressure chamber 431b is low pressure.

  Of course, even if the rotary spring 439 is not provided, if the magnitude relationship between the pressure of the working fluid supplied to the first pressure chamber 431a and the pressure of the working fluid supplied to the second pressure chamber 431b is reversed, The port member 412b can be rotated in both forward and reverse directions. By providing the stoppers 436a and 436b, the rotation range of the port member 412b can be limited. However, in such a configuration, it becomes difficult to use the working fluid used in the expander 303 as a power source for the actuator 406, resulting in a complicated structure. Therefore, it is preferable to use this embodiment.

  Further, according to the rotary spring 439 as described above, the magnitude of the rotational force applied to the piston 430 changes according to the position occupied by the piston 430 in the cylinder 432. The forward (or reverse) rotational force that the differential pressure between the high pressure working fluid supplied to the first pressure chamber 431a and the low pressure working fluid supplied to the second pressure chamber 431b gives to the eccentric portion 412a and the piston 430, The repulsive force by the rotation spring 439, that is, the reverse direction (or forward direction) rotational force applied to the port member 412b is balanced, so that the port member 412b is positioned at a predetermined rotational angle. In this way, by controlling the differential pressure between the working fluid supplied to the first pressure chamber 431a of the actuator 406 and the working fluid supplied to the second pressure chamber 431b, the control to freely displace the port member 412b. Is possible. That is, the second suction hole 412c can be adjusted to an optimum position according to the operating condition of the expander 303.

  As described above, the high-pressure working fluid flows from the suction pipe 53 through the suction passage 437 and flows into the working chamber 55a (see FIG. 2A) from the first suction hole 41b provided in the first cylinder 41. Separately from the path, the high-pressure working fluid flows into the first pressure chamber 431a inside the cylinder 432 via the high-pressure side inflow hole 450 branched from the suction pipe 53, and the second suction fluid provided in the port member 412b. It flows into the working chamber 55a through the hole 412c. As the port member 412b rotates, the position of the second suction hole 412c changes, so that the suction volume of the working fluid to the first cylinder 41 changes.

  In this embodiment, the port member driving eccentric portion 412a and the port member 412b are connected or integrated in the vertical direction parallel to the central axis O. As shown in FIGS. 11 and 12B, the port member 412b has a substantially disk shape, and closes the first cylinder 41 on one main surface, and the port member driving eccentricity on the other main surface side. The port member driving cylinder 432 is closed by being connected (or integrated) with the portion 412a. A portion located on the side farther from the first cylinder 41 is the port member driving eccentric portion 412a, and a portion located on the side closer to the first cylinder 41 is the port member 412b. In this way, the power transmission mechanism from the actuator 406 to the port member 412b can be omitted, which contributes to the suppression of the increase in the number of parts and the simplification of the structure, as well as the highly reliable expander 303. . The port member driving eccentric portion 412a itself can also serve as the port member driving piston 430. In this case, the port member 412b is configured as a part integrated with the port member driving piston 430. can do.

  The positional relationship between the first suction hole 41b and the second suction hole 412c is as described in FIGS. 4A, 4B, and 4C.

  Further, the operation principle of the first cylinder 41 and the second cylinder 42 is as described in FIGS. 5A and 5B.

  The relationship between the rotation angle θ of the shaft 13 and the transition point of each process from suction to discharge is as described with reference to FIG. 6A.

  Further, the relationship between the rotation angle θ of the shaft 13 and the working chamber volume is as described in FIG. 6B.

  Next, a pressure regulator for controlling the pressure of the working fluid supplied to the control pressure pipe 435 of the actuator 406 will be described. A heat pump 300 shown in FIG. 13 includes a compressor 81, a gas cooler 82, the expander 303 described with reference to FIG. 11, an evaporator 84, and a pressure regulator 500A. The pressure regulator 500A adjusts the differential pressure between the high pressure fluid and the low pressure fluid to be supplied to the actuator 406 of the expander 303. By providing such a pressure regulator 500A, the operation of the actuator 406 can be controlled from the outside of the expander 303. In the example of FIG. 13, the pressure regulator 500 </ b> A is installed outside the expander 303, but can be installed inside the expander 303.

  The pressure regulator 500A includes a first pressure pipe 501 having one end connected to the suction pipe 53 of the expander 303, a second pressure pipe 502 having one end connected to the control pressure pipe 435 of the expander 303, and the expander 303. A third pressure pipe 503 having one end connected to the discharge pipe 54 and a hollow housing 513 to which the other ends of the pressure pipes 501, 502, and 503 are connected are provided. That is, the outlet pipe of the radiator 302 is branched into the first pressure pipe 501 and the suction pipe 53 of the expander 303. Further, the discharge pipe 54 and the third pressure pipe 503 of the expander 303 are joined to form an inlet pipe of the evaporator 304. The interior of the housing 513 is partitioned into three pressure adjustment chambers, a first pressure adjustment chamber 504, a second pressure adjustment chamber 505, and a third pressure adjustment chamber 506. A first pressure pipe 501 is connected to the first pressure adjustment chamber 504. A second pressure pipe 502 is connected to the second pressure adjustment chamber 505. A third pressure pipe 503 is connected to the third pressure adjustment chamber 506.

  An elastic body 507 (spring) is disposed in the third pressure adjustment chamber 506. Between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506, there is disposed a piston 508 that partitions both pressure adjustment chambers and one end of which is connected to the elastic body 507. The piston 508 can advance and retreat between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506. The piston 508 is formed with a fine channel 514 that communicates the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506. Between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505, a valve 509 for adjusting the amount of working fluid flowing between the two pressure adjustment chambers is provided. One end of a connecting shaft 512 is connected to the valve 509. The other end of the connecting shaft 512 is connected to the iron core 511. A coil 510 is disposed around the iron core 511. The iron core 511 and the coil 510 constitute a plunger type solenoid.

  In the pressure regulator 500A, the first pressure regulation chamber 504 is equal to the pressure on the high pressure side of the refrigerant circuit, and the third pressure regulation chamber 506 is equal to the pressure on the low pressure side of the refrigerant circuit. Further, the pressure in the second pressure regulation chamber 505 controlled by the pressure regulator 500A is supplied to the control pressure pipe 435 of the expander 303 and used to change the suction volume of the expander unit 400.

  In the configuration as shown in FIG. 13, the connecting shaft 512 has an elastic restoring force of the elastic body 507, a pressure due to the pressure difference between the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506, and a current flowing through the coil 510. The driving force given is added. The connecting shaft 512 stops at a position where these forces are balanced. By changing the current flowing through the coil 510, the pressure in the second pressure regulation chamber 505 can be controlled.

  That is, the pressure regulator 500A acquires a part of the high-pressure working fluid to be sent to the first suction hole 41b of the expander unit 400, and depressurizes the obtained working fluid to thereby reduce the second pressure chamber 431b of the actuator 406. Create a low-pressure working fluid to supply to Then, the pressure of the second pressure chamber 431b formed in the port member driving cylinder 432 is controlled by adjusting the degree of decompression of the working fluid, and is provided in the port member 412b and the port member 412b around the central axis O. The position of the second suction hole 412c is controlled. In this way, the position of the second suction hole 412c can be controlled easily and accurately.

  Thus, the heat pump 300 has one end connected to the main pipe (suction pipe 53) for sending the working fluid to the first suction hole 41b of the expander unit 400, and the other end connected to the pressure regulator 500A. One end is connected to the first pressure pipe 501 that supplies a part of the high-pressure working fluid to be supplied to the first pressure adjustment chamber 504 of the pressure regulator 500A, and the second pressure adjustment chamber 505 of the pressure regulator 500A. Is connected to the actuator 406 (specifically, the control pressure pipe 435), and a second pressure pipe 502 that supplies the low-pressure working chamber 431b (see FIG. 14) of the actuator 406 to the low-pressure working fluid decompressed by the pressure regulator 500A; It has.

  The operation of the pressure regulator 500 will be described. For example, when it is desired to increase the suction volume of the expander 303 (expander unit 400), the current flowing through the coil 510 is increased. Then, the force in the direction of the elastic body 507 acting on the iron core 511 increases, the elastic body 507 is contracted, and the valve 509 narrows the passage between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505. As a result, the pressure in the second pressure adjustment chamber 505 decreases and approaches the pressure in the third pressure adjustment chamber 506. Accordingly, the differential pressure between the pressure in the control pressure pipe 435 and the pressure in the suction pipe 53 increases. The port member driving piston 430 and the port member driving eccentric portion 412a rotate in a direction in which the volume of the second pressure chamber 431b decreases. The second suction hole 412c arrives at the position shown in FIG. 4C, for example. As a result, the suction time of the expander 303 is lengthened and the suction volume is increased according to the principle described in FIGS. 5A and 5B.

  Conversely, when it is desired to reduce the suction volume of the expander 303 (expander unit 400), the current flowing through the coil 510 is decreased. Then, the force in the direction of the elastic body 507 acting on the iron core 511 decreases, the length of the elastic body 507 increases, and the valve 509 widens the passage between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505. As a result, the pressure in the second pressure adjustment chamber 505 increases and approaches the pressure in the first pressure adjustment chamber 504. Accordingly, the differential pressure between the pressure in the control pressure pipe 435 and the pressure in the suction pipe 53 decreases. The port member driving piston 430 and the port member driving eccentric portion 412a rotate in a direction in which the volume of the second pressure chamber 431b increases. The second suction hole 412c arrives at the position shown in FIG. 4A, for example. As a result, the suction time of the expander 303 is shortened and the suction volume is reduced according to the principle described in FIGS. 5A and 5B.

  It is also possible to employ a pressure regulator configured as shown in FIG. First, as shown in FIG. 14, a fine passage 440 that bypasses the control pressure pipe 435 and the suction pipe 53 is provided in the actuator 406 ′. As shown in FIG. 15, the pressure regulator 500B includes a housing 515, a coil 510, an iron core 511, a connecting shaft 512, a piston 516, and an elastic body 507 (spring). The interior of the housing 515 is partitioned into two pressure adjustment chambers 520 and 521. A valve 509 that adjusts the amount of working fluid flowing between the two adjusting chambers is disposed between the two pressure adjusting chambers 520 and 521. The coil 510 and the iron core 511 constitute a plunger type solenoid. The elastic body 507 biases the valve 509 in a direction to open through the piston 516. On the other hand, when a current is passed through the coil 510, the iron core 511 biases the valve 509 in a closing direction via the connecting shaft 512. That is, the opening degree of the valve 509 can be controlled by controlling the current flowing through the coil 510. According to the opening degree of the valve 509, the pressure in the pressure adjusting chamber 521 to which the control pressure pipe 435 is connected can be changed.

  In the examples of FIGS. 13 and 15, it is necessary to keep the control pressure by constantly flowing the working fluid little by little, and the recovery efficiency of the expansion energy is inevitably lowered. Therefore, if the control pressure is made with the configuration shown in FIG. 16A, the recovery efficiency of the expansion energy can be further increased.

  A pressure regulator 500C illustrated in FIG. 16A includes a housing 560 that is partitioned into three pressure regulation chambers, a first pressure regulation chamber 561, a second pressure regulation chamber 562, and a third pressure regulation chamber 563. Yes. A first pressure pipe 501 through which the working fluid before expansion flows is connected to the first pressure adjustment chamber 561. Connected to the second pressure adjustment chamber 562 is a second pressure pipe 502 that communicates the second pressure adjustment chamber 562 and the second pressure chamber 431 b (see FIG. 12A) of the actuator 406 in the expander 303. A third pressure pipe 503 through which the expanded working fluid flows is connected to the third pressure adjustment chamber 563. A first valve 580 is disposed between the first pressure adjustment chamber 561 and the second pressure adjustment chamber 562. The first valve 580 can be controlled to open and close by driving a plunger type solenoid constituted by the coil 570, the iron core 573, the elastic body 584 (spring), and the connecting shaft 576. By opening the first valve 580, high-pressure working fluid can be sent into the second pressure regulating chamber 562. On the other hand, a second valve 581 is disposed between the second pressure adjustment chamber 562 and the third pressure adjustment chamber 563. Similar to the first valve 580, the second valve 581 can be controlled to open and close by a plunger type solenoid constituted by a coil 571, an iron core 574, an elastic body 585 (spring) and a connecting shaft 577. By opening the second valve 581, the working fluid can be sent from the second pressure adjustment chamber 562 to the third pressure adjustment chamber 563. That is, by controlling the opening and closing of the two (plural) valves 580 and 581, a control pressure between the pressure of the working fluid before expansion and the pressure of the working fluid after expansion is created, and the second pressure It becomes possible to maintain the inside of the adjustment chamber 562 and thus the second pressure chamber 431b of the actuator 406 at the generated control pressure. When the pressure in the second pressure regulating chamber 562 is higher than the desired pressure, the first valve 580 is closed and the second valve 581 is opened. When the pressure is lower than the desired pressure, the first valve 580 is opened and the second valve 581 is opened. The two valve 581 is closed.

  Further, as shown in the block diagram of FIG. 16B, the pressure regulator 500C includes a pressure sensor 590 that detects the pressure in the second pressure adjustment chamber 562, and the valves 580 and 581 based on the detection result of the pressure sensor 590. A controller 591 that controls opening and closing may be provided. The pressure sensor 590 may be disposed in the second pressure chamber 431b of the actuator 406 in the expander 303. The controller 591 acquires a sensor signal from the pressure sensor 590, and calculates the difference between the target pressure value and the current pressure value. When the calculated difference is not within the predetermined allowable range, the opening and closing of the first valve 580 and the second valve 581 are controlled so that the difference becomes small. Specifically, when the current pressure value is smaller than the target pressure value, the solenoid on the first valve 580 side is driven for a certain period of time, and a certain amount of high-pressure working fluid is discharged from the first pressure adjustment chamber 561. It flows into the second pressure adjustment chamber 562. Conversely, when the current pressure value is larger than the target pressure value, the solenoid on the second valve 581 side is driven for a certain period of time, and the working fluid is transferred from the second pressure adjustment chamber 562 to the third pressure adjustment chamber 563. Move.

  By repeatedly performing such processing, the pressure in the second pressure adjusting chamber 562 can be quickly and accurately adjusted to a desired pressure. Since there is no need to constantly flow current through the solenoids (coils 570 and 571) that open and close the first valve 580 and the second valve 581, the power consumption of the pressure regulator 500C can be suppressed, and the recovery efficiency of the expansion energy of the working fluid It is advantageous for improvement. If a program for periodically monitoring the input from the pressure sensor 590 is incorporated in the controller 591, even if a pressure fluctuation occurs due to unavoidable leakage of the working fluid, the second pressure adjustment chamber 562 It is possible to automatically restore the desired pressure to the desired pressure.

(Third embodiment)
As described in the first embodiment, the features of the expander shown in the second embodiment are suitably used for an expander-integrated compressor in which the expander unit and the compressor unit are integrated via a shaft. can do. FIG. 17 is a longitudinal sectional view of such an expander-integrated compressor.

  The expander-integrated compressor 700 includes a hermetic container 11, a scroll-type compressor unit 20 disposed on the upper side of the hermetic container 11, and a two-stage rotary type disposed on the lower side of the hermetic container 11. The expander section 400, the rotary motor 12 disposed between the compressor section 20 and the expander section 400, and the shaft 13 shared by the compressor section 20, the expander section 400, and the rotary motor 12. I have. When the rotary motor 12 rotates the shaft 13, the compressor unit 20 operates. In the expander-integrated compressor 700, the rotational force applied to the shaft 13 when the working fluid (refrigerant) expands in the expander unit 400 is used as auxiliary power for the compressor unit 20. Since the expansion energy of the working fluid is directly transmitted to the compressor unit 20 without once being converted into electric energy, high energy recovery efficiency can be expected.

  As described in the second embodiment, the expander unit 400 includes the port member 412b provided with the second suction hole 412c for changing the suction volume, and the actuator 406 for rotationally displacing the port member 412b. I have. The structures and functions of the port member 412b and the actuator 406 are as described in the second embodiment.

  Further, the basic structure and operation principle of the compressor unit 20 and the expander unit 400 are also as described in the first embodiment.

  According to the expander-integrated compressor 700 of FIG. 17, the actuator 406 is driven by the pressure difference between the working fluid provided by the control pressure pipe 435 and the working fluid provided by the suction pipe 53, and the position (center of the port member 412b) The rotation angle around the axis O can be changed. By controlling the position of the port member 412b, the suction volume of the expander unit 400 can be freely controlled. According to such a heat pump using the expander-integrated compressor 700, the flow rate of the working fluid flowing through the expander unit 400 can be freely controlled without providing a bypass circuit, and thus a highly efficient heat pump. The system can be realized.

(Fourth embodiment)
The actuator incorporated in the expander of the second embodiment can be suitably employed in the expander or the expander-integrated compressor, but can be configured as a rotary actuator for another application.

  FIG. 18 is a longitudinal sectional view of a rotary actuator according to the fourth embodiment. 19 is a cross-sectional view taken along the line D5-D5 of FIG. As shown in FIGS. 18 and 19, the rotary actuator 800 includes a cylinder 806, a shaft 801 that passes through the inside and outside of the cylinder 806, a piston 807 that rotates eccentrically in the cylinder 806 and rotates the shaft 801, and the cylinder 806 and the piston And a vane 812 that partitions the pressure chamber 808 formed between the first pressure chamber 808a and the second pressure chamber 808b.

  The shaft 801 has an eccentric portion 802 that bulges outward in the radial direction at an intermediate portion thereof, and has one end passing through the upper end plate 803 and the other end passing through the lower end plate 804. A closing member 805 is disposed below the lower end plate 804. The upper end plate 803 and / or the closure member 805 may include a bearing for the shaft 801. The eccentric portion 802 of the shaft 801 is disposed inside the cylinder 806 and is fitted with a ring-shaped piston 807.

  The rotary actuator 800 includes a vane 812, a spring 809, a suction pipe 810, and a control pressure pipe 811. The vane 812 is reciprocally held in a vane groove provided in the cylinder 806 so that the tip is in contact with the piston 807. The spring 809 biases the vane 812 toward the piston 807. A first inflow hole 820 connected to the first pressure chamber 808a and a second inflow hole 821 connected to the second pressure chamber 808b are formed in the upper end plate 803 that covers the upper side of the cylinder 806. A suction pipe 810 is connected to the first pressure chamber 808a via a first inflow hole 820. A control pressure pipe 811 is connected to the second pressure chamber 808b via a second inflow hole 821. A force is applied to the piston 807 due to a pressure difference between the first fluid flowing into the first pressure chamber 808a and the second fluid flowing into the second pressure chamber 808b, and the eccentric portion 802, and thus the entire shaft 801, rotates. A first stopper 813a and a second stopper 813b are formed on the inner peripheral surface of the cylinder 806 at a predetermined angle in the circumferential direction. These stoppers 813a and 813b limit the rotation range when the piston 807 rotates due to the pressure difference of the working fluid.

  In this embodiment, an elastic body that gives a repulsive force to the rotation of the shaft 801 is not provided, but an elastic body (rotation spring 439: see FIG. 12B) as described in the second embodiment may be provided. Good. By doing so, it is possible to control the rotation angle of the shaft 801 by adjusting the differential pressure between the first fluid that flows into the first pressure chamber 808a and the second fluid that flows into the second pressure chamber 808b. It becomes. Note that the first fluid and the second fluid may be the same type of fluid or different types of fluid. As such a fluid, for example, oil in a hydraulic circuit, refrigerant in a refrigerant circuit, or air in a pneumatic circuit can be used.

  As described above, the expander of the present invention provides an efficient means for recovering the expansion energy of the working fluid in the refrigeration cycle, and in particular, achieves high efficiency of the heat pump using the expander-integrated compressor. , Has great utility value.

The longitudinal cross-sectional view of the expander integrated compressor in the 1st Embodiment of this invention D1-D1 sectional drawing of the expander part of the expander integrated compressor of FIG. D2-D2 sectional view of the expander portion of the expander-integrated compressor of FIG. The partial cutaway perspective view of the fixing | fixed part of the upper end plate of the expander part of the expander integrated compressor of FIG. The perspective view of the movable part of the upper end plate of the expander part of the expander integrated compressor of FIG. Partial cutaway perspective view of the upper end plate integrating the fixed part and the movable part The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. The elements on larger scale of the D1-D1 cross section of the expander part of the expander integrated compressor of FIG. Operational principle diagram of the first cylinder of the expander part of the expander-integrated compressor of FIG. Operational principle diagram of the second cylinder of the expander portion of the expander-integrated compressor of FIG. The figure which shows the relationship between the rotation angle of the shaft in the expander part of the expander integrated compressor of FIG. 1, and each stroke of a working chamber. The figure which shows the relationship between the rotation angle of the shaft in the expander part of the expander integrated compressor of FIG. 1, and a working chamber volume. Mollier diagram of refrigeration cycle using the expander-integrated compressor of FIG. PV diagram showing the relationship between pressure and working chamber volume in the expander section of the expander-integrated compressor of FIG. Configuration diagram of heat pump using expander integrated compressor Configuration diagram of a heat pump using a separate expander Graph illustrating the relationship between generator efficiency and generator speed The longitudinal cross-sectional view of the expander in the 2nd Embodiment of this invention D3-D3 sectional view of the expander of FIG. D4-D4 cross section of the expander of FIG. FIG. 11 is a configuration diagram of a heat pump including the expander and the pressure regulator in FIG. Cross section of actuator modification Configuration diagram of a modification of the pressure regulator Configuration of another modification of the pressure regulator The block diagram of the example which provides a pressure sensor in the pressure regulator of FIG. 16A Vertical section of an expander-integrated compressor according to a third embodiment of the present invention Cross section of rotary actuator D5-D5 sectional view of the rotary actuator of FIG. Configuration diagram of a heat pump using a conventional expander-integrated compressor Mollier diagram of a heat pump using a conventional expander-integrated compressor

Claims (25)

A cylinder,
A shaft having an eccentric part;
A piston that fits into the eccentric part and rotates eccentrically inside the cylinder;
N rotary expansion mechanisms (n is an integer of 2 or more) having a partition member for partitioning the space between the cylinder and the piston into a suction side space and a discharge side space;
A first suction hole for sucking the working fluid into the suction side space of the first expansion mechanism;
a communication hole that connects the discharge side space of the kth expansion mechanism (k is an integer from 1 to n-1) and the suction side space of the (k + 1) th expansion mechanism to form one space;
a discharge hole for discharging the working fluid from the discharge side space of the nth expansion mechanism;
A connection position with the suction side space of the first expansion mechanism is variable, and a second suction hole for sucking the working fluid into the suction side space;
With an expander. An intermediate plate disposed between the cylinder of the k-th expansion mechanism and the cylinder of the (k + 1) -th expansion mechanism;
The cylinder of the first expansion mechanism is provided with the first suction hole, the intermediate plate is provided with the communication hole, and the cylinder of the nth expansion mechanism and / or a closing member for closing the cylinder are provided. The expander according to claim 1, wherein the discharge hole is provided. A closing member for closing the end face of the cylinder of the first expansion mechanism;
The expander according to claim 1, wherein the second suction hole is provided in the closing member. The closing member includes a movable part capable of rotating around the shaft as a rotation center,
The expander according to claim 3, wherein the second suction hole is provided in the movable part.   The expander according to claim 4, wherein the movable portion includes a cylindrical bearing surface that supports the shaft.   The expander according to claim 4, further comprising a drive mechanism for rotating the movable part.   The expander according to claim 6, wherein the drive mechanism includes an electric actuator.   A first inflow path for supplying a working fluid from the outside of the expander to the second suction hole provided in the movable portion, a branch from the first inflow path, and a supply of the working fluid to the first suction hole 5. The expander according to claim 4, wherein the closing member further includes an annular fixed portion that is provided in the interior of the second inflow passage and that the movable portion is rotatably combined.   An expander-integrated compressor, comprising: an expander unit comprising the expander according to claim 1; and a compressor unit integrally connected to the expander unit via the shaft.   A heat pump comprising the expander according to claim 1.   A heat pump comprising the expander-integrated compressor according to claim 9. A movable member that closes the cylinder of the first expansion mechanism and is rotatable independently of the shaft around the shaft;
An actuator that applies a rotational force of a magnitude based on a differential pressure between the high-pressure fluid and the low-pressure fluid to the movable member,
The expander according to claim 1, wherein the movable member is provided with the second suction hole.   The expander according to claim 12, wherein a working fluid is used as the high-pressure fluid and the low-pressure fluid.   The expander according to claim 12, wherein the actuator, the movable member, and the first expansion mechanism are arranged in this order in a direction parallel to the central axis of the shaft. A suction path connected to the first suction hole for sending a working fluid to the cylinder of the first expansion mechanism;
A branch path branched from the inhalation path,
The high-pressure chamber of the actuator and the branch path are connected, and a high-pressure working fluid supplied to the actuator through the branch path is used as the high-pressure fluid.
Further, the actuator and the movable member are arranged adjacent to each other so that one end of the second suction hole is connected to the high pressure chamber of the actuator,
The expansion according to claim 12, wherein the working fluid supplied to the actuator as the high-pressure fluid is supplied to the suction side space of the first fluid mechanism through the second suction hole provided in the movable member. Machine. The actuator is
A movable member driving cylinder;
A movable member driving piston for rotating the movable member by forming a pressure chamber between the movable member driving cylinder and eccentrically swinging in the movable member driving cylinder;
A movable member driving partition member that divides the pressure chamber into a high pressure chamber into which the high pressure fluid flows and a low pressure chamber into which the low pressure fluid flows;
The expander of claim 12, comprising:   The movable member has a substantially disk shape, and the main surface of the first expansion mechanism is closed on one main surface, and the movable member driving piston or the movable member driving surface is closed on the other main surface. The expander according to claim 16, wherein the movable member driving cylinder is closed by being connected to or integrated with an eccentric portion disposed inside the piston.   A stop that is provided on the inner peripheral surface of the movable member driving cylinder, has a convex shape toward the central axis of the shaft, and limits the movable range of the movable member driving piston in the movable member driving cylinder. The expander of claim 16 further comprising:   The expander according to claim 16, further comprising a biasing unit that biases the movable member in a predetermined rotation direction. The biasing means is configured so that the magnitude of the rotational force applied to the movable member changes according to the position occupied by the movable member around the central axis of the shaft,
By balancing the forward rotational force applied to the movable member drive piston by the differential pressure between the high pressure fluid and the low pressure fluid, and the reverse rotational force applied to the movable member by the biasing means, The expander of claim 19, wherein the position of the movable member about the central axis of the shaft is controlled.   An expander-integrated compressor, comprising: an expander unit including the expander according to claim 12; and a compressor unit integrally connected to the expander unit via the shaft.   A heat pump comprising the expander according to claim 12.   The heat pump according to claim 22, further comprising a pressure regulator that adjusts a differential pressure between the high-pressure fluid and the low-pressure fluid supplied to the actuator.   The pressure regulator acquires a part of the working fluid to be sent to the first suction hole, creates the low-pressure fluid by decompressing the obtained working fluid, and adjusts the degree of decompression, thereby The heat pump according to claim 23, wherein the position of the second suction hole around the central axis of the shaft is controlled.   One end is connected to the main pipe for sending the working fluid to the first suction hole, the other end is connected to the pressure regulator, and a part of the high-pressure working fluid to be expanded is supplied to the first chamber of the pressure regulator. One end is connected to the first pressure pipe to be supplied to the second chamber and the second chamber of the pressure regulator, the other end is connected to the actuator, and the working fluid depressurized by the pressure regulator is reduced in pressure to the actuator. The heat pump according to claim 23, further comprising a second pressure pipe that supplies the low pressure chamber.

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