WO2007052569A1

WO2007052569A1 - Expander and heat pump using the same

Info

Publication number: WO2007052569A1
Application number: PCT/JP2006/321561
Authority: WO
Inventors: Hiroshi Hasegawa; Masaru Matsui; Atsuo Okaichi; Tomoichiro Tamura; Takeshi Ogata; Keizo Matsui; Tetsuya Matsuyama
Original assignee: Matsushita Electric Industrial Co., Ltd.
Priority date: 2005-10-31
Filing date: 2006-10-27
Publication date: 2007-05-10
Also published as: EP1953337A8; EP1953337A4; US20090282845A1; JPWO2007052569A1; EP1953337A1; JP4065316B2

Abstract

A expander having n number of rotary fluid mechanisms (n is an integer number equal to or greater than 2), a first suction hole (41b) for sucking operation fluid into a suction side space (55a) of a first fluid mechanism (41), a communication hole (43a) for connecting a discharge side space (55b) of a k-th fluid mechanism (k is an integer number from 1 to n-1) and a (k + 1)-th suction side space (56a) to form one space, and a discharge hole (51a) for discharging the operation fluid from the discharge side space of an n-th fluid mechanism. The position at which the first fluid mechanism (41) is connected to the suction side space (55a) is changeable, and the expander further has a second suction hole (72f) for sucking the operation fluid into the suction side space (55a).

Description

Expander and heat pump using the same

Technical field

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

Background art

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).

[0003] 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, a compressor gas cooler (radiator) 2, an expander 3 and an evaporator 4 constitute a main circuit 8 of working fluid (coolant). Compressor 1, expander 3, and 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 joins 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. Then, after expanding to low temperature and low pressure (gas-liquid two phase) in the expander 3 or the expansion valve 5, it is heated by the evaporator 4 and returned to low temperature and low pressure (gas phase). The expander 3 collects the expansion energy of the working fluid and converts it into rotational energy of the shaft 7. This rotational energy is used as part of the work for driving the compressor 1, and as a result, the power of the rotary motor 6 can be reduced.

[0006] 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. [0007] When 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 at the inlet side of the compressor 1 and the expansion machine 3 The volumetric flow rate of the working fluid at the inlet side is (Vcs XN) and (Ves XN), respectively. Since the mass flow rate of 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. When 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 are expressed as (GZ ( Vcs XN)}, {GZ (Ves XN)}. From these equations, the ratio of the working fluid density on the inlet side of the compressor 1 and the working fluid density on the inlet side of the expander 3 is {G / (Ves XN)} Z {GZ (Ves XN)}, That is, (VesZVcs) is 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. The density ratio of the working fluid at point A on the inlet side of compressor 1 and point C on the inlet side of expander 3 is constant at (VesZVcs), so the density of working fluid at point A is / 0. Then the density p at point C is (VcsZVes). Point A

0 c 0

Assuming that the density is constant, increasing the pressure at point C will change from point C to point C 'on the line = (Vcs / V es). That is, point C is isothermal

0

It becomes impossible to change to the point C "which is increased by the pressure along the line (T = T), and the free control of the refrigeration cycle is impeded. The refrigeration cycle has a coefficient of performance ( Since there is an optimum high pressure that maximizes (COP) (for example, Japanese Laid-Open Patent Publication No. 2002-81766), efficient operation cannot be performed unless 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. This is because the volume flow rate ratio is 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).

[0010] 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 same rotation speed of the compressor and the expander, The working fluid must flow to the sub circuit provided with the expansion valve together with the main circuit provided with the expander. However, this cannot recover the expansion energy of the working fluid that passes through the subcircuit.

[0011] Although the expansion energy of the working fluid cannot be efficiently recovered! /, The problem becomes prominent when an expander-integrated compressor is used, but the separation type is not connected to the compressor by a shaft. It also occurs when using an expander. When a separate 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 the distance from the rated speed increases, it is desirable to operate the generator near the rated speed. However, in the refrigeration cycle, it is difficult to operate the generator only in the vicinity of the rated speed because the circulation amount and density of the working fluid change according to the operating conditions. For this reason, it is not easy to efficiently collect the expansion energy of the working fluid even in the separation type expander.

Disclosure of the invention

[0012] The present invention has been made in view of the above circumstances, and an object thereof is to provide an expander that can efficiently recover the expansion energy of a working fluid. Another object of the present invention is to provide a heat pump including the expander.

[0013] That is, the present invention provides

A cylinder,

A shaft having an eccentric part;

A piston that fits into the eccentric part and rotates eccentrically inside the cylinder; and a partition member for partitioning a space between the cylinder and the piston into a suction side space and a discharge side space. N rotary expansion mechanisms (n is an integer of 2 or more), a first suction hole for sucking working fluid into the suction side space of the first expansion mechanism, and kth (k from 1 to n-1) A communication hole that connects the discharge side space of the expansion mechanism 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 n-th expansion mechanism;

A connection position of the first expansion mechanism with the suction side space is variable, and a second suction hole for sucking the working fluid into the suction side space; An expander is provided.

[0014] The present invention also relates to an expander-integrated type, 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. Provide a compressor.

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 working fluid suction process force shifts to the working fluid expansion process by changing the connection position between the suction side space of the first expansion mechanism and the second suction hole. The timing can be adjusted to control the ratio of the length of time the inflation process takes place to the length of time the inhalation process takes place. For this reason, according to the present invention, it is possible to change the above (VesZV cs). 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 introducing the entire amount of the working fluid into the expander without providing the auxiliary circuit for the working fluid.

When the expander of the present invention is used as a separate 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, the rotational speed of the generator connected to the expander is made close to the rated rotational speed, and it becomes easy to maintain high power generation efficiency by the generator.

Brief Description of Drawings

FIG. 1 is a longitudinal sectional view of an expander-integrated compressor according to a first embodiment of the present invention.

[Fig. 2A] D1-D1 cross section of the expander section of the expander-integrated compressor of Fig. 1

[Fig. 2B] D2-D2 cross section of the expander section of the expander-integrated compressor of Fig. 1

FIG. 3A is a partial cutaway perspective view of a fixed portion of an upper end plate of the expander portion of the expander-integrated compressor of FIG.

3B is a perspective view of the movable part of the upper end plate of the expander part of the expander-integrated compressor of FIG.

FIG. 3C is a partially cut perspective view of the upper end plate in which the fixed part and the movable part are integrated.

[Fig. 4A] Partial enlarged view of the D1-D1 cross section of the expander section of the expander-integrated compressor of Fig. 1

[FIG. 4B] Partial enlarged view of the D1-D1 cross section of the expander part of the expander-integrated compressor of FIG. [4C] D1—D1 cross-sectional enlarged view of the expander section of the expander-integrated compressor in FIG.

[FIG. 5A] Operation principle diagram of the first cylinder of the expander unit of the expander-integrated compressor of FIG. 1 B 5B] Operation principle diagram of the second cylinder of the expander unit of the expander-integrated compressor of FIG. 6A] A diagram showing the relationship between the rotation angle of the shaft and each stroke of the working chamber in the expander section of the expander-integrated compressor of FIG.

[6B] Diagram showing the relationship between the rotation angle of the shaft and the working chamber volume in the expander section of the expander-integrated compressor in FIG.

圆 7] Mollier diagram of the refrigeration cycle using the expander-integrated compressor in Figure 1

[Fig. 8] PV diagram showing the relationship between pressure and working chamber volume in the expander section of the expander-integrated compressor in Fig. 1

[9A] Heat pump configuration diagram using an expander-integrated compressor

[9B] Heat pump configuration diagram using a separate expander

[Figure 10] Graph illustrating the relationship between generator efficiency and generator speed

[11] Longitudinal sectional view of the expander according to the second embodiment of the present invention

[Fig. 12A] D3-D3 cross section of expander in Fig. 11

[Fig. 12B] D4-D4 cross section of expander in Fig. 11

圆 13] Configuration diagram of heat pump with expander and pressure regulator of Fig. 11

[Fig.14] Cross-sectional view of a modification of the actuator

[Fig. 15] Configuration diagram of a modified pressure regulator

[Fig. 16A] Configuration of another modification of the pressure regulator

[FIG. 16B] Block diagram of an example in which a pressure sensor is provided in the pressure regulator of FIG. 16A

圆 17] Longitudinal sectional view of the expander-integrated compressor according to the third embodiment of the present invention

[Fig.18] Cross section of rotary actuator

[Fig.19] D5—D5 cross section of rotary actuator in Fig.18

圆 20] Heat pump configuration diagram using a conventional expander-integrated compressor

21] Mollier diagram in a heat pump using a conventional expander-integrated compressor BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings. [0020] (First embodiment)

FIG. 1 is a longitudinal sectional view showing the configuration of the expander-integrated compressor according to the first embodiment of the present invention. FIG. 2A is a cross-sectional view taken along the line D1-D1 of the expander portion of the expander-integrated compressor of FIG. Cross-sectional view, Fig. 2B is a cross-sectional view of the expander section in the D2-D2 cross section, Fig. 3A is a partial cut-away perspective view of the fixed portion of the upper end plate of the expander section, and Fig. 3B is the upper end 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 together.

[0021] The expander-integrated compressor 100 in the present embodiment 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 thereof. , The rotary motor 12 including the rotor 12a and the stator 12b disposed between the compressor unit 20 and the expander unit 40, the compressor unit 20, the expander unit 40, and the rotary electric motor. And a shaft 13 for connecting the machine 12. The shaft 13 may be formed by connecting a plurality of parts on one axis.

The scroll compressor unit 20 includes a fixed scroll 21, an orbiting scroll 22, an old 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 constrained to rotate by the Oldham ring 23 has a spiral wrap 22a meshing with the lap 21a of the fixed scroll 21, while the shaft The crescent-shaped working chamber 28 formed between the wraps 21a and 2 2a is swung along with the rotation of 13 and the volume is reduced while moving from the outside to the inside. Compress working fluid. The compressed working fluid passes through the discharge hole 21b provided in the center of the fixed scroll 21, the inner space 25a of the muffler 25, and the flow path 29 passing through the fixed scroll 21 and the bearing member 24 in this order. It is discharged into the internal space 11a of the sealed container 11. 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 or centrifugal force while staying in the inner space 11a. .

[0023] 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 further includes a Fitted to the eccentric part 13b of the shaft 13 and held in a reciprocating manner in the first piston 44 that rotates eccentrically in the first cylinder 41 and the vane groove of the first cylinder 41, one end is The first vane 46 that contacts the first piston 44, the first spring 48 that contacts the other end of the first vane 46, and urges the first vane 46 toward the first piston 44, and the second cylinder 42 are The second piston 45 that engages with the eccentric portion 13c of the shaft 13 and moves eccentrically in the second cylinder 42 is reciprocally held in the vane groove of the second cylinder 42. A second vane 47 whose portion 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. .

[0024] 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 arranged 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 also hold the first cylinder 41 with vertical force, and the middle plate 43 and the lower end plate 51 hold the second cylinder 42 with vertical force. Due to the holding by the upper end plate 73, the middle plate 43 and the lower end plate 51, there is a working chamber whose volume changes in accordance with the rotation of the pistons 44 and 45 in the first cylinder 41 and the second cylinder 42. It is formed. The upper end plate 73 and the lower end plate 51 are closing 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.

[0026] As shown in FIGS. 2A and 2B, inside the first cylinder 41, a suction side working chamber 55a (first suction side space) and a first piston 44 and a first vane 46, and The discharge side working chamber 55b (first discharge side space) is partitioned by the second piston 45 and the second vane 47 inside the second cylinder 42, and the suction side working chamber 56a (second suction side space) ) And discharge-side working chamber 56b (second discharge-side space) are formed. The total volume of the two working chambers 56a, 56b in the second cylinder 42 is equal to the two working chambers 55a, 55 in the first cylinder 41. It is larger than the total volume of b. 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. ). After the high-pressure working fluid flows into the working chamber 55a, it 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 71f 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 an inner diameter smaller than the cylindrical concave surface 71a, and a stepped surface 71c connecting the cylindrical concave surfaces 71a and 71b. And surrounded by When the fluid machine (expander-integrated compressor 100) is assembled, the central axis 70 coincides with the central axis of the shaft 13.

[0028] Inside the fixed portion 71 are an inflow path 71d (first inflow path) and an inflow path that is a branch path from the inflow path 71d as an inflow path that leads the working fluid from the suction pipe 53 to the working chamber 55a. 71e (second inflow channel). 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. 1 It communicates with the suction side working chamber 55a in the cylinder 41.

[0029] 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 is formed on the cylindrical concave surface 71a of the fixed portion 71 as an outer peripheral surface. A cylindrical convex surface 72b that contacts, 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. ing. 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 part 72 further includes a channel groove 72d that circulates along the circumferential direction on the cylindrical convex surface 72b, and a second suction hole 72f connected to the channel 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 operates on the suction side in the first cylinder 41. Room 5 5a [Communicate!

As shown in FIG. 3C, the fixed portion 71 and the movable portion 72 are integrated by the movable portion 71 being rotatably fitted in the through hole 71f of the fixed portion 71. Stepped surface 71c of fixed part 71 and movable part 72 The stepped surfaces 72g abut against each other to prevent the movable portion 72 from coming out above the fixed portion 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.

[0031] 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 the constant density ratio in the compressor with an expander integrated type.

[0032] As described with reference to FIG. 3A, FIG. 3B, and FIG. 3C, the second suction hole 72f defines the end face of the first cylinder 41 included in the first fluid mechanism into which the working fluid flows first. It may be provided on the end plate 73 as a closing member to be closed. This is because the movable second suction hole 72f can be configured with a simple configuration. Further, 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 composed of a plurality of parts.

[0033] Further, as described above, at least a part of the end plate 73 may be the movable part 72 that can rotate around the shaft 13 and the movable part 72 may be provided with the second suction hole 72f. Preferred V ,. This is because it is easy to ensure a large movement range of the second suction hole 72f.

In this embodiment, the cylindrical bearing surface on which the movable portion 72 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 path 71d (first first) for supplying 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) and 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 are provided inside. The movable portion 72 is rotatably joined to such a fixed portion 71. By providing the two inflow passages 71d and 71e inside the fixed portion 71, piping for guiding the working fluid to the second suction hole 72f becomes unnecessary, which is advantageous for space saving inside the sealed container 11. . In addition, since the inflow passages 71d and 71e are provided inside the fixed portion 71, there is a problem of leakage of the working fluid. Hard to occur.

[0036] Returning to FIG. On the fixed portion 71 of the upper end plate 73, a gear 75 that meshes with the gear 72e of the rotating portion 72, a rotary motor 76 (electric actuator) that drives the gear 75, and a force plate are installed. The movable portion 72 is driven by the rotary motor 76 via the gears 72e and 75. As described above, 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 hermetic container 11 and controls the rotation angle of the movable part 72, and receives a control signal from the controller to move the movable part 72. To control the connection position to the working chamber 55a. If a stepping motor or servo motor is used as the rotary motor 76, the position of the second suction hole 72f can be controlled with high accuracy. Further, a detector (for example, an encoder) for detecting the rotation angle of the movable part 72 may be provided. As a driving means for the movable portion 72, a means other than the rotary motor 76, for example, an actuator that uses a pressure difference of fluid may be used.

[0037] 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 4 lb in which the connection position to the working chamber 55a is fixed from the intake pipe 53 to the first working chamber 55a and the working chamber 55a is variable. The working fluid is supplied via a second suction hole 72f. It is not necessary to place flow control mechanisms such as openable / closable solenoid valves and differential pressure valves in these two paths.

[0038] The working fluid sucked into the first cylinder 41 passes through the second cylinder 42, discharge holes 51a provided in the lower end plate 51, the inner space 52a of the muffler 52, the first and second cylinders 41, , 42 are discharged from the discharge pipe 54 to the refrigeration cycle via the flow path 57 penetrating 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 also configured with, for example, a metal thin plate force, and is disposed so as to close the discharge hole 51a with the internal space 52a side force of the muffler 52. The discharge valve 74 is connected to the upstream side (second cylinder This is a differential pressure valve that opens when the pressure in the discharge chamber 42b on the discharge side of the compressor 42 becomes higher than the pressure on the downstream side (on 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 respect to the position of the first vane 46 around the shaft 13, and is 20 ° (Fig. 4A), 90 ° (Fig. 4B), 180 ° (Fig. Each is adjusted to 4C). More precisely, the angle φ is the rotation direction of the shaft 13 about the central axis 70 (shown in the figure) on the first straight line 80 connecting the contact point between the first vane 46 and the first piston 44 and the central 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, 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 42. On the other hand, the position of the second suction hole 72f can be arbitrarily set between 0 ° force 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. 5 図 shows an operation principle diagram of the second cylinder 42 corresponding to the above. . Here, the rotational angle Θ of the shaft 13 is 0 ° when the contact force between the first cylinder 41 and the first piston 44 is at the so-called top dead center located at the first vane 46, and the rotational direction of the shaft 13 Clockwise is displayed as positive.

[0042] The working fluid flows into the working chamber 55a generated after Θ = 0 ° from the first suction hole 41b after Θ = 20 °. After 0 = 90 °, the working fluid flows into the working chamber 55a from the first suction hole 41b and the second suction hole 72f. After passing through 0 = 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 0 = 380 ° (not shown), the contact between the first cylinder 41 and the first piston 44 passes through the first suction hole 41b, and the working chamber 55b and the first suction hole Communication with 41b is lost. In the conventional two-stage rotary expander, the suction process of the working fluid is completed at this point.

[0043] On the other hand, since the second suction hole 72f is provided in the expander unit 40 of the present embodiment, the working fluid does not flow from the second suction hole 72f even when Θ = 380 °. continue. This swelling In the tensioning unit 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 inhalation process is complete.

[0044] 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.The second cylinder 42 is higher in the axial direction than the first cylinder 41, and the volume is larger. Increases at a rate. 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 reaching 0 = 700 ° (not shown), the contact between the second cylinder 42 and the second piston 45 passes through the discharge hole 5 la, and the working chamber 56 a communicates with the discharge hole 5 la. At this point, the expansion process ends.

[0045] When the expansion process is completed, the discharge process of the working fluid is started. At 0 = 720 °, the working chamber 55b disappears, the working chamber 56a changes to the working chamber 56b, and as the shaft 13 rotates, the volume of the working chamber 56b decreases and the working fluid is discharged from the discharge hole 51a. The At 0 = 1080 °, the working chamber 56b disappears and the discharge process ends.

[0046] 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 °. Show about. As is apparent from the above description, the rotation angle Θ of the shaft 13 at which the suction process ends is the angle at which the contact point between the first cylinder 41 and the first piston 44 passes the second suction hole 72f for the second time. It becomes. This angle can be expressed as Θ = (360 + φ). Therefore, as the angle φ of the second suction hole 72f increases, the timing of shifting to the suction process force expansion process is delayed, and the expansion process becomes shorter as the suction process becomes longer. 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 is a force that moves in the order of the working chamber 55a, the working chamber 55b, the working chamber 56a, and the working chamber 56b. On the vertical axis in the figure, the suction volume Ves φ, which 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 °, 180 °, and the discharge process start time Indicates the discharge volume Ved, which is the volume of the working chamber. The suction volume Ves φ increases with increasing φ, but the discharge volume Ved is constant regardless of φ. [0048] 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. As a result, the suction volume Ves φ, which is the volume at the end of the suction process of the working chambers 55a, 55b, 56a, 56b, was made variable. As a result, the density ratio (Vcs / Ves φ) of the working fluid on the inlet side of the compressor unit 20 and the expander unit 40 can be controlled.

[0049] FIG. 7 illustrates a Mollier diagram of a refrigeration cycle using the expander-integrated compressor of the present embodiment. Since the density ratio can be changed, the point C corresponding to the state of the inlet side of the two-stage rotary expander section 40 is changed to the pressure along the isotherm (T = 35 ° C in the example shown). It can be changed and moved to point or point C〃. In this way, the temperature and pressure on the inlet side of the two-stage rotary type expander section 40 can be freely controlled, which is not possible with a conventional refrigeration cycle using an expander-integrated compressor. A good refrigeration cycle can be operated.

[0050] In particular, as in the present embodiment, the second suction hole 72f is formed in the movable part 72 that can rotate around the axis of the shaft 13, and the angle φ can be adjusted to 0 ° force to 360 °. Because of the wide control range, it is easy to improve the efficiency of the refrigeration cycle.

[0051] Next, the effect of providing the discharge valve 74 in the discharge hole 51a will be described. Figure 8 shows the relationship between the working chamber volume and pressure (PV diagram). The subscript φ of the symbol in the figure is the angle φ of the second suction hole 72f. Point P φ represents the start of the expansion process, point S φ represents the end of the expansion process, and point T represents the start of the discharge process. In addition, since a refrigeration cycle using carbon dioxide acid as the working fluid is assumed, the inflection point Q φ due to phase change is shown during the expansion process.

[0052] Since the discharge volume Ved is constant, the volume ratio (= VedZVes φ) before and after the expansion process decreases as the suction volume Ves φ increases as the second suction hole 72f moves, and the expansion process ends. When the pressure S φ increases. For this reason, for example, when the range of the angle φ of the second suction hole 72f is controlled in the range of 20 ° force and 180 °, the pressure S at the end of the expansion process when the maximum angle 180 ° is selected is the low pressure of the refrigeration cycle. To be lower than side pressure Ped

180

It is desirable to design so that underexpansion does not occur. This is because when the underexpansion occurs, a part of the energy due to the pressure difference of the working fluid cannot be recovered.

[0053] With this design, overexpansion occurs at least when the angle φ is set to 180 ° or less. Arise. Overexpansion is a phenomenon in which the pressure Ρφ becomes lower than the low-pressure side pressure Ped of the refrigeration cycle. When overexpansion occurs, an overexpansion loss occurs because the working fluid is pushed out from the discharge hole 51a into the inner space 52a of the muffler 52, which has a higher pressure than the inside of the working chamber 56b. The magnitude of the overexpansion loss can be shown by the area of the triangle S φ における in Fig. 8.

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 volume of the working chamber 56b decreases as the shaft 13 rotates. If the discharge valve 74 is arranged in the discharge hole 51a, the discharge fluid does not open until the pressure in the working chamber 56b, which has decreased due to overexpansion, becomes equal to the low-pressure side pressure Pd of the refrigeration cycle. Recompressed in 5b. 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 be rotatable about the shaft 13 in the same direction as the rotation direction of the shaft 13. This is because the movable part 72 can be rotated with a small amount of power by the frictional force between the shaft 13 and the movable part 72. According to this, it becomes easy to reduce the size of the rotary motor 76 and store it in the sealed container 11.

In the present embodiment, when the movable part 72 rotates 360 °, it returns to the original position. For this reason, it is easy to control the rotary electric motor 76 that only needs to rotate the movable part 72 in the same direction at all times. The frictional force between the shaft 13 and the movable part 72 does not interfere with the rotational drive.

[0058] In this embodiment, since the suction volume Ves φ of the expander unit 40 is variable, the expander unit 40 is not used! / And the compressor unit 20 has a normal structure used in the refrigeration cycle. Since the compressor unit 20 can use the normal structure as it is, the development cost can be reduced.

[0059] When the expander-integrated compressor of the present embodiment is used, the expander unit 40 rotates in the same rotation as the compressor unit 20 while controlling the circulation amount of the working fluid in the refrigeration cycle by the rotation speed of the compressor unit 20. The suction volume Ves φ can be adjusted according to the operating conditions while rotating by a number. Therefore The role of the compressor unit 20 and the expander unit 40 in the control of the refrigeration cycle can be shared, and the control algorithm of the refrigeration cycle using the expander-integrated compressor can be facilitated.

[0060] The type of working fluid used in the expander-integrated compressor of the present embodiment is not limited, but 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 a constant density ratio becomes remarkable.

[0061] In the present embodiment, the second suction hole 72f movable with the first suction hole 41b is provided, but the number of movable suction holes may be two or more. The suction volume Ves φ is determined by the suction hole arranged at the side position. 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 body 88 (refrigerant pipe) that connects them together. In the conventional example shown in FIG. 20, the subcircuit 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 subcircuit is essential. Is not necessary. However, a sub-circuit may be provided for other purposes, for example, for stably starting and stopping the heat pump.

[0063] 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 the configuration of a power recovery heat pump using a separate 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 is supplied. Equipped with a circulating pipe 88 (refrigerant pipe)! 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 speed Nr, the speed is determined from the rated speed. The further away, the lower the power generation efficiency. 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, the circulating volume and density of the working fluid change, so it is difficult to operate the expander with a constant suction volume Ves only near the rated speed Nr. 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 Ves φ.

[0065] (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. An actuator that utilizes the pressure difference between fluids is highly reliable in harsh environments such as high temperature and 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 above-mentioned actuator. In the present embodiment, a suction volume variable type expander including such an actuator will be described. In the present embodiment, the same reference numerals are used for the same parts as those described in the first embodiment.

FIG. 11 is a longitudinal sectional view of the expander in 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 disposed 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.

[0067] 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 a second suction hole 412c for a follower. 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 differential pressure 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 suction process of the working fluid to the expansion process changes, and the time for the expansion process to the length of time for the suction process to be performed is changed. The length ratio changes.

[0068] As the high-pressure fluid and low-pressure fluid that are the power source of the actuator 406, a working fluid to be expanded by the expander 303 can be used. 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 not required. 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, in the direction parallel to the central axis O of the shaft 13, 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. They are arranged side by side. Such an arrangement is advantageous for the small expander 303 because it is possible to suppress the size expansion due to the provision of the actuator 406 and the port member 412b as much as possible.

[0070] 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 hermetic container 11, and a rotor 86a disposed inside the stator 86b. A shaft 13 is fixed to the center of the rotor 86a. The shaft 13 extends downward from the rotor 13a and is shared by the expander unit 400.

[0071] 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 portion of the shaft 13, and an oil supply passage (not shown) is formed in the shaft 13 and in the Z or outer peripheral portion. When the shaft 13 rotates, the lubricating oil in the oil sump 405 is pumped up by the oil pump and supplied to each sliding portion of the expander unit 400 through the oil supply passage.

[0072] 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 412b has a substantially disk shape with a hole through which the shaft 13 penetrates at the center, and is disposed inside the housing 413 whose outer shape substantially coincides with the first cylinder 41. The housing 413 restricts the displacement of the port member 412b in the radial direction in which the inner diameter of the housing 413 and the outer diameter of the port member 412b are substantially equal. 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 412b rotates, the second suction hole 412c moves in the rotation direction of the shaft 13.

[0074] FIG. 12A is a cross-sectional view of the expander D3-D3 shown in FIG. 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, A suction pipe 53 and a control pressure pipe 435 are provided. 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 part of the actuator 406.

As shown in FIG. 12A, the eccentric portion 412a 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 in the cylinder 432 (specifically, eccentrically swing) 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 held in a vane groove provided in the cylinder 432 so as to be able to reciprocate so that the tip thereof is in contact with the piston 430. Spring 434 biases vane 433 toward piston 430.

[0078] The pressure chambers 431a and 431b formed inside the cylinder 432 are separated by vanes 433. It is separated into two spaces, a pressure chamber 431a and a second pressure chamber 431b. Further, the cylinder 4 32 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 the inside and outside of the cylinder 432, respectively. A suction pipe 53 is connected to the first pressure chamber 431a through a high-pressure side inflow hole 450. The suction pipe 53 supplies the high-pressure working fluid before expansion to the first pressure chamber 43 la. 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 the second pressure chamber 431b with a working fluid having a lower pressure than the working fluid supplied to the first pressure chamber 431a side. The differential pressure between the first pressure chamber 431a and the second pressure chamber 43 lb gives a rotational force to the piston 430. The piston 430 that receives the rotation force from the differential pressure of the working fluid rotates the eccentric portion 412a and the port member 412b.

[0079] The cylinder 432 is supplied with working fluid from the suction pipe 53 through the upper end plate 424, through the cylinder 432, the housing 413, and the first cylinder 41 to the working chamber 55a of the first cylinder 41. A suction passage 437 for inhalation 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 sends the working fluid (refrigerant) to the first cylinder 41. And a high-pressure side inlet hole 450 as a branch path branched from the suction path 437. The high-pressure chamber 43 la of the actuator 406 is connected to the high-pressure side inflow hole 450, and the high-pressure working fluid supplied to the actuator 406 through the high-pressure side inflow hole 450 is used as a 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. The working fluid force supplied to the actuator 406 as fluid 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 there is no inconvenience when the characteristics of the refrigeration cycle change due to mixing of different types of fluids. Also, the working fluid used in the expander 303 is the power source of the actuator 406. By doing so, it is not necessary to supply energy such as external power, which is advantageous in improving the recovery efficiency of the expansion energy of the working fluid.

[0082] Further, on the inner peripheral surface of the cylinder 432, a first strobe 436a and a second stover 436b having a convex shape directed toward the central axis O of the shaft 13 are provided at a predetermined angle in the circumferential direction. ing. These Stono 436a and 436b are piston 430 force working fluid pressure difference (when the working fluid (refrigerant) is carbon dioxide, during rated operation, the high pressure side is about lOMPa and the low pressure side is about 3-5MPa. ) To limit the movable range (rotation angle around central axis O) when rotating. As a result, the port member 412b is allowed to rotate only within a predetermined angle range (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 a structure in which the piston 430 rotates eccentrically as in the present embodiment, a space for forming the second suction hole 412c penetrating the port member 412b up and down can be secured, and the expander It is also advantageous for downsizing.

FIG. 12B is a D4-D4 cross-sectional view 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 in 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 urging direction of the rotary spring 439 is determined according to the volume of the first pressure chamber 431a. The decreasing direction, that is, the direction of the second suction hole 412c is set to approach the first suction hole 41b (see FIG. 2A). By such a function of the rotary spring 439, the position of the port member 412b can be continuously changed within the movable range defined by the Stotto 436a and 436b. Further, it is possible to rotate the port member 412b 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. .

[0085] Of course, even when the rotary spring 439 is not provided, 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. By rotating, 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.

Furthermore, 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. Forward (or reverse) rotational force applied to the eccentric part 412a and the piston 430 by the differential pressure between the high-pressure working fluid supplied to the first pressure chamber 43 la and the low-pressure working fluid supplied to the second pressure chamber 431b Then, the repulsive force of 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, the port member 412b can be freely displaced by adjusting 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. Control becomes possible. That is, the second suction hole 412c can be adjusted to an optimal 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 this path, the high-pressure working fluid flows into the first pressure chamber 431a inside the cylinder 432 via the high-pressure side inlet hole 450 branched from the suction pipe 53, and the second suction provided in the port member 412b. It flows into the working chamber 55a through the inlet 412c. As the port member 412b rotates, the position of the second suction hole 412c changes, so 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 integrally connected in the vertical direction parallel to the center axis O. As shown in FIGS. 11 and 12B, the port member 412b has a substantially disc 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 drive cylinder 432 is closed by connecting (or integrally) with the portion 412a. The part located farther from the first cylinder 41 is the port member drive eccentric part 412a. The portion located on the near side is a 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 suppression of the increase in the number of parts and simplification of the structure, and in turn, a highly reliable expander 303 can be provided. It becomes like this. The port member drive eccentric part 412a itself can also serve as the port member drive piston 430. In this case, the port member 412b is integrated with the port member drive piston 430. Can be configured as a part.

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

[0090] The operating principles of the first cylinder 41 and the second cylinder 42 are as described in Figs. 5A and 5B.

[0091] 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 in FIG. 6A.

[0092] The relationship between the rotation angle Θ of the shaft 13 and the working chamber volume is as described with reference to 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 in 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 that should 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 also by the external force of the expander 303. In the example of FIG. 13, the pressure regulator 500A is installed outside the expander 303 !, but can also be installed inside the expander 303.

[0094] 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 an expansion A third pressure pipe 503 having one end connected to the discharge pipe 54 of the machine 303 and a hollow housing 513 to which the other ends of the pressure pipes 501, 502, 503 are connected. 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. In addition, the discharge pipe 54 of the expander 303 and the third pressure pipe 503 merge to form the inlet pipe of the evaporator 304. The The interior of the housing 513 is divided 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.

[0095] 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 has one end connected to the elastic body 507. The piston 508 can move back and forth 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 allows the second pressure adjustment chamber 505 and the third pressure adjustment chamber 506 to communicate with each other. Between the first pressure adjustment chamber 504 and the second pressure adjustment chamber 505, a valve 509 for adjusting the amount of the 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 arranged 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 adjustment chamber 504 is equal to the pressure on the high pressure side of the refrigerant circuit, and the third pressure adjustment chamber 506 is equal to the pressure on the low pressure side of the refrigerant circuit. Further, the pressure in the second pressure adjustment 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 includes an elastic restoring force of the elastic body 507, a pressure due to a pressure difference between the second pressure adjusting chamber 505 and the third pressure adjusting chamber 506, and a coil 510. And the driving force given by the current flowing through it. 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 regulating chamber 505 can be controlled.

That is, the pressure regulator 500A obtains a part of the high-pressure working fluid to be sent to the first suction hole 41b of the expander unit 400, and decompresses the obtained working fluid to obtain the actuator 406. This produces a low-pressure working fluid that supplies the second pressure chamber 431b. Then, the pressure of the second pressure chamber 431b formed in the port member driving cylinder 432 is controlled by adjusting the degree of pressure reduction of the working fluid, and the port member 412b around the central axis O is controlled. And the position of the second suction hole 412c provided in the port member 412b. In this way, the position of the second suction hole 412c can be controlled easily and accurately.

[0099] In this manner, 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 4 lb 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 connected to the first pressure adjustment chamber 504 of the pressure regulator 500A and the second pressure adjustment chamber 505 of the pressure regulator 500A. The other end is connected to the actuator 406 (specifically, the control pressure pipe 435), and the working fluid reduced in pressure by the pressure regulator 500A is supplied to the low pressure chamber 431b (see FIG. 14) of the actuator 406. 2 pressure pipes 502.

[0100] 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. Along with this, the pressure difference 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. For example, the second suction hole 412c arrives at the position shown in FIG. 4C. 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.

[0101] 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. As a result, the pressure difference 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 4 12a rotate in a direction in which the volume of the second pressure chamber 431b increases. For example, the second suction hole 412c arrives at the position shown in FIG. 4A. As a result, in accordance with the principle explained in FIGS. 5A and 5B, the suction time of the expander 303 is shortened and the suction volume is reduced. [0102] It is also possible to employ a pressure regulator configured as shown in FIG. First, as shown in FIG. 14, a minute 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. Between both pressure adjusting chambers 520 and 521, a valve 509 for adjusting the amount of working fluid flowing between the two adjusting chambers is disposed. The coil 510 and the iron core 511 constitute a plunger type solenoid. The elastic body 507 biases the valve 509 through the piston 516 in the opening direction. On the other hand, when an electric current is passed through the coil 510, the iron core 511 biases the valve 509 in the 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. Depending on 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, since it is necessary to constantly flow the working fluid little by little to maintain the control pressure, the recovery efficiency of the expansion energy is inevitably lowered. Therefore, if the control pressure is generated with the configuration shown in FIG. 16A, the recovery efficiency of the expansion energy can be further increased.

[0104] The pressure regulator 500C shown in FIG. 16A has 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. It is equipped with. Connected to the first pressure adjusting chamber 561 is a first pressure pipe 501 through which the working fluid before expansion flows. Connected to the second pressure adjustment chamber 562 is a second pressure pipe 502 that communicates with the second pressure adjustment chamber 562 and the second pressure chamber 431b (see FIG. 12A) of the actuator 406 in the expander 303. Yes. 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 opening and closing of the first valve 580 can be controlled 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, a high-pressure working fluid can be fed 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. As with valve 1 580, valve 281 Is controlled 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. In other words, by controlling the opening and closing of the two (multiple) 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, It becomes possible to maintain the inside of the second pressure regulating chamber 562, and thus the inside of 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, while when the pressure is lower than the desired pressure, the first valve 580 is turned on. Open and close second valve 581.

In addition, 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 a detection result of the pressure sensor 590. A controller 591 that controls opening and closing of the valves 580 and 581 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 the 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 transferred to the first pressure regulating chamber 561. To flow into the second pressure regulating chamber 562. Conversely, if 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 to change from the second pressure adjustment chamber 562 to the third pressure adjustment chamber 563. Move working fluid

By repeatedly performing such processing, the pressure in the second pressure adjustment 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, 571) that open and close the first valve 580 and the second valve 581, the power consumption of the pressure regulator 500 C can be suppressed, and the expansion energy of the working fluid can be reduced. It is advantageous for improving the collection efficiency. In addition, if a program that periodically monitors the input from the pressure sensor 590 is installed in the controller 591, the pressure changes due to unavoidable leakage of the working fluid. Even if movement occurs, the pressure in the second pressure regulating chamber 562 can be automatically restored to a desired pressure.

[0107] (Third embodiment)

As described in the first embodiment, the features of the expander shown in the second embodiment are preferably 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.

[0108] The expander-integrated compressor 700 is disposed in the hermetic container 11, the scroll-type compressor unit 20 disposed on the upper side of the hermetic container 11, and the lower side in the hermetic container 11. Common to the two-stage rotary expander unit 400, the rotary motor 12 disposed between the compressor unit 20 and the expander unit 400, and the compressor unit 20, the expander unit 400, and the rotary motor 12 1 and 3 shafts. The rotary motor 12 rotates the shaft 13 to operate the compressor unit 20. 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. The High energy recovery efficiency can be expected because the expansion energy of the working fluid is directly transmitted to the compressor unit 20 without being converted into electric energy.

[0109] 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 rotational displacement of the port member 412b. Actuator 406. The structures and functions of the port member 412b and the actuator 406 are as described in the second embodiment.

[0110] 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.

[0111] According to the expander-integrated compressor 700 of Fig. 17, the actuator 406 is driven by the pressure difference between the working fluid given by the control pressure pipe 435 and the working fluid given by the suction pipe 53, and the port member 412b The position of (the rotation angle around the central 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 the heat pump using the expander-integrated compressor 700, the flow rate of the working fluid flowing through the expander section 400 without providing a bypass circuit. As a result, it is possible to realize a highly efficient heat pump system.

[0112] (Fourth embodiment)

The actuator incorporated in the expander of the second embodiment can be suitably used for the expander or the expander-integrated compressor, but can be configured as a rotary actuator for another use.

[0113] FIG. 18 is a longitudinal sectional view of a rotary actuator that can be applied to the fourth embodiment. FIG. 19 is a cross-sectional view taken along the line D5-D5 in FIG. As shown in FIGS. 18 and 19, the rotary actuator 800 includes a cylinder 806, a shaft 801 that penetrates the inside and outside of the cylinder 806, a piston 807 that rotates eccentrically in the cylinder 806 and rotates the shaft 801, and a cylinder 806. A vane 812 that partitions a pressure chamber 808 formed between the piston 807 into a first pressure chamber 808a and a second pressure chamber 808b is provided.

[0114] The shaft 801 has an eccentric portion 802 that bulges radially outward at an intermediate portion thereof, and has one end that penetrates the upper end plate 803 and the other end that penetrates the lower end plate 804. ing. A closing member 805 is disposed below the lower end plate 804. Upper end plate 803 and Z or closure member 805 may include bearings for 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.

[0115] 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 81 2 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 eventually the shaft 801 rotate. . In addition, on the inner peripheral surface of the cylinder 806, the circumferential direction A first stagger 813a and a second stagger 813b are formed at a predetermined angle apart from each other. These stoppers 813a and 813b limit the rotation range when the piston 807 rotates due to the pressure difference of the working fluid.

[0116] 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 (rotary spring 439: see FIG. 12B) as described in the second embodiment is provided. You may do it. By doing so, it is possible to control the rotation angle of the shaft 801 by adjusting the differential pressure between the first fluid flowing into the first pressure chamber 808a and the second fluid flowing 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. Industrial applicability

[0117] As described above, the expander of the present invention provides an efficient means of recovering the expansion energy of the working fluid in the refrigeration cycle, and in particular, the high efficiency of the heat pump using the expander-integrated compressor. It has a great utility value as a means to realize a kite.

Claims

The scope of the claims

[1] a cylinder;

A shaft having an eccentric part;

A connection position of the first expansion mechanism with the suction side space is variable, and a second suction hole for sucking the working fluid into the suction side space;

With an expander.

[2] It further includes an intermediate plate that is disposed between the cylinder of the k-th expansion mechanism and the cylinder of the (k + 1) -th expansion mechanism, and partitions both of them.

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 and Z of the nth expansion mechanism or a closing member for closing the cylinder 2. The expander according to claim 1, wherein the discharge hole is provided.

[3] The expander according to claim 1, further comprising a closing member that closes an end face of the cylinder of the first expansion mechanism, wherein the closing member is provided with the second suction hole.

4. The expander according to claim 3, wherein the closing member includes a movable part capable of rotating about the shaft as a rotation center, and the second suction hole is provided in the movable part.

5. The expander according to claim 4, wherein the movable part includes a cylindrical bearing surface that supports the shaft.

6. The expander according to claim 4, further comprising a drive mechanism that rotates the movable part.

7. The expander according to claim 6, wherein the drive mechanism includes an electric actuator.

[8] External force of the expander The working fluid is supplied to the second suction hole provided in the movable part. A first inflow passage to be supplied and a second inflow passage that branches from the first inflow passage and supplies the working fluid to the first suction hole are provided inside, and an annular shape in which the movable portion is rotatably combined. The expander according to claim 4, wherein the closing member further includes a fixing portion.

[9] An expander-integrated compressor, comprising: an expander unit comprising the expander according to claim 1; and a compressor unit that is integrally connected to the expander unit via the shaft.

[10] A heat pump comprising the expander according to claim 1.

[11] A heat pump comprising the expander-integrated compressor according to claim 9.

[12] A movable member that closes the cylinder of the first expansion mechanism and is rotatable independently of the shaft with the shaft as a rotation center;

An actuator that provides the movable member with a rotational force having a magnitude based on a differential pressure between the high-pressure fluid and the low-pressure fluid;

The expander according to claim 1, wherein the second suction hole is provided in the movable member.

13. The expander according to claim 12, wherein a working fluid is used as the high-pressure fluid and the low-pressure fluid.

14. The expander according to claim 12, wherein the actuator, the movable member, and the first expansion mechanism force are arranged in this order in a direction parallel to the central axis of the shaft.

[15] A suction path connected to the first suction hole and 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 is connected to the branch path, and a high-pressure working fluid supplied to the actuator through the branch path is used as the high-pressure fluid. Further, one end of the second suction hole is connected to the branch of the actuator. The actuator and the movable member are arranged adjacent to each other so as to be connected to the high pressure chamber,

13. 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.

[16] 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 oscillating 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:

[17] The movable member has a substantially disc 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 is movable on the other main surface. 17. The expander according to claim 16, wherein the movable member driving cylinder is closed by being connected to or integrally formed with an eccentric portion arranged inside the member driving piston.

[18] The movable member driving piston is provided on an inner peripheral surface of the movable member driving cylinder, has a convex shape toward the central axis of the shaft, and a movable range of the movable member driving piston in the movable member driving cylinder. The expander according to claim 16, further comprising a stagger that restricts the pressure.

19. The expander according to claim 16, further comprising a biasing unit that biases the movable member in a predetermined rotation direction.

[20] The biasing means is configured such 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 driving 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, 20. The expander according to claim 19, wherein the position of the movable member around the central axis of the shaft is controlled.

[21] An expander-integrated compressor comprising the expander portion having expander force according to claim 12, and a compressor portion integrally connected to the expander portion via the shaft.

[22] A heat pump comprising the expander according to claim 12.

23. 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.

[24] The pressure regulator obtains a part of the working fluid to be sent to the first suction hole, and creates the low-pressure fluid by depressurizing the obtained working fluid. 24. The heat pump according to claim 23, wherein the position of the second suction hole around the central axis of the shaft is controlled by adjusting.

[25] 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 pressure regulator. One end of the first pressure pipe supplied to the first chamber and the second chamber of the pressure regulator are connected to one end, the other end is connected to the actuator, and the working fluid is reduced in pressure by the pressure regulator. The heat pump according to claim 23, further comprising: a second pressure pipe that supplies the pressure to the low pressure chamber of the actuator.