WO2006057212A1

WO2006057212A1 - Fluid machine and heat pump employing it

Info

Publication number: WO2006057212A1
Application number: PCT/JP2005/021349
Authority: WO
Inventors: Masaru Matsui; Hiroshi Hasegawa; Atsuo Okaichi; Takeshi Ogata; Tomoichiro Tamura
Original assignee: Matsushita Electric Industrial Co., Ltd.
Priority date: 2004-11-25
Filing date: 2005-11-21
Publication date: 2006-06-01

Abstract

A compressor integrated with an expander, having a constant high operation efficiency by reducing the bypass pipeline, embodying valve control, reducing the dead space on the suction side, and recovering power from high-pressure working fluid while eliminating the operation condition (restriction) of density ratio=constant . A fluid machine comprising a compressor section (12) for compressing a working fluid sucked into a compression chamber (13) by rotating a drive shaft (14) and an expander section (20) for producing the rotational power of a power recovery shaft (26) by expanding the working fluid sucked into a working chamber (25) is further provided with a sensor (48) for detecting delivery pressure of a delivery chamber (33) and a solenoid valve (40) located at a suction port (27) immediately in front of the inlet of the working chamber (25) and controlling the communication between the suction port (27) and the working chamber (25). High operation efficiency can be ensured constantly without providing a bypass pipeline and without causing deterioration in expansion efficiency due to over expansion or dead space by varying open/closure timing of the solenoid valve (40) such that the quantity of working fluid introduced into the working chamber (25) is a target quantity determined from the delivery pressure obtained from the delivery pressure sensor (48) and a target suction pressure for maximizing the refrigeration cycle efficiency.

Description

Fluid machine and heat pump device using the same

Technical field

The present invention relates to an expander-integrated fluid machine connected to an expander that supplies a high-pressure working fluid to generate rotational power, and a heat pump device using the expander-integrated fluid machine.

Background art

FIG. 11 shows a system configuration of a conventional general power recovery type air conditioner. In FIG. 11, the system includes a condenser 101, an evaporator 102, a compressor 103, and an expander 104. The compressor 103 compresses the working fluid and an expansion that generates rotational power from the high-pressure working fluid. The machine 104 is connected to the motor 105 in one axis. In other words, the expander 104 is configured to generate rotational power by ideally entropy expansion of the high-pressure working fluid and directly assist the driving power of the compressor 103. The reason why the compressor 103 and the expander 104 are connected to each other is that the structure is simple and the power recovery loss is small.

In such a conventional air conditioner, Fig. 12 shows how the refrigeration cycle changes when the working fluid is carbon dioxide. In the Mollier diagram (p-h diagram) in Fig. 12, 1 → 2 is the compression process in which the working fluid is compressed and raised from the low pressure P1 to the high pressure Ph in the compressor 103, and 2 → 3 is in the condenser 101. 3 → 4 is the expansion process in which the working fluid is expanded from the high pressure Ph to the low pressure P1 in the expander 104 to recover the power, and 4 → 1 is the isobaric heat absorption process in the evaporator 102. Show.

However, in the above configuration in which the compressor 103 and the expander 104 are connected to one shaft, the compressor 103 and the expander 104 always rotate at the same rotation speed, and therefore the system is operated with a constant refrigerant circulation rate. Operating conditions (constraints) of the working fluid “density ratio = constant” occur, for example, it is difficult to properly control the discharge pressure (high pressure Ph) of the compressor 103 that affects the efficiency of the system. For this reason, high-efficiency operation cannot always be realized. Therefore, as a technique for eliminating such an operation condition (constraint) of “density ratio = constant”, there is a known technique described in Patent Document 1. Figure 13 shows another conventional air conditioner system. The configuration is shown. In the present air conditioner, a bypass pipe 112 is provided between the discharge pipe 110 and the suction pipe 111 of the expander 104, and the passage area of the bypass pipe 112 is adjusted to increase or decrease. A control valve 106 is provided.

The air conditioner having such a configuration performs the following operations.

A target value of the discharge temperature of the compressor 103 is set, and then the opening degree of the control valve 106 is controlled so that the discharge temperature of the compressor 103 becomes the target value. When the control valve 106 is controlled in the closing direction, the amount of working fluid passing through the bypass line 112 decreases, and the amount of working fluid entering the expander 104 increases. Conversely, when the control valve 106 is controlled to open, the amount of working fluid that passes through the bypass line 112 increases, and the amount of working fluid that enters the expander 104 decreases. Thus, by controlling the opening degree of the control valve 106, the operating conditions of the system can be freely determined so as to obtain high operating efficiency while using the expander 104.

As another technique for eliminating the operation condition (constraint) of “density ratio = constant”, there is a known technique described in Patent Document 2. In this technology, the pressure after the expansion of the working fluid is reduced under the operating conditions where the ratio of the high pressure to the low pressure of the system (pressure ratio) is smaller than the pressure ratio assumed in the design of the expander. This is to prevent the amount of recovered power from falling below the pressure (loss due to overexpansion). That is, the communication passage is branched from the working fluid inflow side of the expander and communicates with the suction Z expansion process position of the expander, and the communication passage is provided with a valve for controlling the passage of the working fluid. When the conditions arise, the valve is opened to allow a part of the working fluid to flow into the expander, increasing the amount of working fluid entering the expander, and increasing the pressure of the working fluid after expansion.

As another technique, there is a known technique described in Patent Document 3. That is, the carbon dioxide supercritical refrigeration cycle rotary expansion device (not shown) is mainly composed of a cylinder body, a rolling piston, an eccentric cam shaft, a pedestal, and an electromagnetic valve. The inner chamber of the expansion device is divided into two high-pressure chambers and two low-pressure chambers by the main / sub bearings and the intermediate partition plate. Carbon dioxide enters the expansion cylinder, moves the force eccentric cam shaft, changes the volume of the expansion cylinder, lowers the fluid pressure, and outputs mechanical power. Through the electric circuit control system, the intake time of the expansion device is controlled by outputting a signal based on the rotation angle of the eccentric cam shaft and controlling the opening of the electromagnetic valve, and this causes the power generation cycle to be performed. Patent Document 1: JP 2001-116371 A

Patent Document 2: JP 2004-197640 A

Patent Document 3: Patent CN1164904C

Disclosure of the invention

Problems to be solved by the invention

[0003] However, in the technique of Patent Document 1 described above, the power recovery cannot be performed for the working fluid passing through the bypass line, and the potential energy of the high-pressure working fluid is unconditionally discarded. I was supposed to do it. Further, although the technique of Patent Document 2 is configured to prevent the occurrence of overexpansion, it does not describe a specific valve control method for realizing it. Furthermore, in the technique of Patent Document 3, the expansion efficiency is reduced because the electromagnetic valve is outside the housing and the dead space on the intake side is large.

[0004] Accordingly, the present invention solves the above-described conventional problems, and eliminates the restriction condition of “density ratio = constant” without providing a bypass pipe, and further provides valve control that prevents overexpansion. In addition, by reducing the dead space on the intake side, it is possible to recover the maximum power from the high-pressure working fluid and to provide an expander-integrated fluid machine that always obtains high operating efficiency. As a goal!

Means for solving the problem

The fluid machine of the present invention has a compression chamber and a drive shaft, and compresses the working fluid sucked into the compression chamber by rotating the drive shaft, and the expansion chamber and the expansion chamber. It has a suction hole that guides the working fluid with pressure, a discharge hole that discharges the working fluid from the expansion chamber, and a power recovery shaft connected to the drive shaft. The working fluid sucked into the expansion chamber is expanded to expand the power recovery shaft. An expander unit for obtaining rotational power, a sealed container having a compressor unit and an expander unit disposed therein, and a suction valve for controlling the amount of working fluid introduced into the expansion chamber in the sealed container. It is a thing. According to the present embodiment, the dead space between the suction valve and the expansion chamber can be reduced, and the amount of working fluid introduced into the expansion chamber by the suction valve can be controlled with high operating efficiency.

The fluid machine of the present invention detects the expander discharge pressure of the working fluid discharged by the discharge hole force. The pressure of the suction valve and the amount of working fluid guided from the suction hole to the expansion chamber become a target amount determined from the expander suction pressure and the expander discharge pressure that maximize the refrigeration cycle efficiency. And an opening / closing timing control means for controlling the opening / closing timing. According to the present embodiment, an expander-integrated fluid machine capable of always obtaining high operating efficiency can be obtained by varying the opening / closing timing of the suction valve so that the expansion chamber has an ideal volume. provide.

The fluid machine of the present invention includes a suction temperature sensor that measures the suction temperature of the working fluid sucked into the suction hole, and a discharge temperature sensor that measures the discharge temperature of the working fluid discharged from the discharge hole. The expansion machine suction pressure is obtained from the discharge temperature. According to the present embodiment, the target suction pressure that maximizes the refrigeration cycle efficiency can be obtained by calculation.

The fluid machine of the present invention includes a discharge temperature sensor that measures the discharge temperature of the working fluid discharged from the discharge hole, and the discharge temperature force also obtains the expander discharge pressure, and the working fluid guided from the suction hole to the expansion chamber And an opening / closing timing control means for controlling the opening / closing timing of the intake valve so that the amount of air reaches the target amount obtained from the expander suction pressure and the expander discharge pressure that maximize the refrigeration cycle efficiency. It is. According to this embodiment, it can be linked to cost reduction.

In the fluid machine of the present invention, the suction valve is an electromagnetic valve. According to the present embodiment, the opening / closing timing can be easily measured, and the problem of non-inflation can be prevented.

In the fluid machine according to the present invention, the opening timing at which the suction valve is opened from the closed time is defined as the suction start time at which the volume of the expansion chamber is minimized, and the closing timing at which the suction valve is opened from the closed time is determined from the suction start time to the expansion chamber. It is configured to have a control function that sets the time until the volume reaches the volume corresponding to the target amount. According to the present embodiment, the brake loss can be minimized, and the volume of the expansion chamber into which the working fluid is introduced can be set to an ideal volume.

The fluid machine of the present invention is provided with a working fluid state holding unit that holds the relationship between the volume and pressure of the working fluid when expanding in the expansion chamber, and the operation that the working fluid state holding unit holds The target amount is obtained using the relationship between the volume of the fluid and the pressure. According to the present embodiment, the relationship between the volume of the working fluid and the pressure can be an approximate expression of a practical expansion process, for example, and higher operating efficiency can be obtained.

The fluid machine of the present invention operates using a working fluid that expands from a supercritical phase to a liquid phase or a gas-liquid two phase.

The fluid machine of the present invention is operated using a working fluid mainly composed of carbon dioxide.

The fluid machine of the present invention is provided with a discharge valve in the first discharge hole of the expander. According to the present embodiment, it is possible to prevent occurrence of overexpansion loss.

In the fluid machine of the present invention, the discharge valve is a reed valve, and the discharge valve opens when the pressure in the expansion chamber reaches a predetermined value. According to the present embodiment, the reed valve automatically opens when the pressure reaches a predetermined value, and recompression is possible so as not to cause an overexpansion loss.

The heat pump device according to the present invention controls the opening / closing timing of the intake valve so that the amount of the working fluid guided to the expansion chamber becomes a target amount that maximizes the refrigeration cycle efficiency. According to the present embodiment, the operation efficiency of the heat pump device can always be increased.

The invention's effect

[0006] According to the fluid machine of the present invention and the heat pump device using the fluid machine, the opening / closing timing of the suction valve can be controlled, and the amount of working fluid guided to the expansion chamber can be set to a target amount that provides high operating efficiency. , By reducing bypass pipe lines, realizing valve control, reducing dead space on the intake side, etc., and eliminating the operating conditions (constraints) of “density ratio = constant” while maximizing from working fluid of high pressure Power recovery is always possible, and high operation efficiency can be obtained at all times.

Brief Description of Drawings

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

FIG. 2 is a cross-sectional view of an expander section in the compressor of the present embodiment

[Fig. 3] PV diagram of the working chamber when the solenoid valve is normally open in this embodiment FIG. 4 is a diagram showing the relationship between the opening / closing timing of the solenoid valve and the flow rate of the working fluid entering the working chamber in the present embodiment.

FIG. 5 is a perspective view of an angle detection gear in the compressor of the present embodiment.

[6] A longitudinal sectional view of the compressor according to the second embodiment of the present invention.

圆 7] Cross section of the compressor shown in Fig. 6 along the line XX

[8] Vertical sectional view of the compressor according to the third embodiment of the present invention.

9] Cross-sectional view of the expander section in the compressor of the present embodiment

[Fig. 10] PV line in the working chamber when the opening and closing timing of the solenoid valve in this embodiment is changed

[Fig. 11] System configuration of conventional air conditioner

圆 12] Mollier diagram when the working fluid is diacid-carbon in the conventional air conditioner

[FIG. 13] System configuration diagram of another conventional air conditioner

Explanation of symbols

10 Airtight container

12 Compressor section

13 Compression chamber

14 Drive shaft

15, 73 rotor

16 Motor section

17 Stator

18 Rotor

20 Expansion unit

21, 71 cylinders

22 Small gap

23 Rotor

24, 74 Vane

25 rooms 26, 76 Power recovery shaft

27 Suction hole

28 Discharge hole and first discharge hole

29 Second discharge hole

30 Valve mechanism

30a reed valve

30b valve stop

31 Kano Kuichi

32 Inhalation route

33 Discharge chamber

34 Discharge path

35 Suction tube

36 Discharge pipe

40 Solenoid valve

45 Angle detection gear

48 Discharge pressure sensor

50 Suction temperature sensor

51 Discharge temperature sensor

52 Gap sensor

60 Solenoid valve controller

61 Working fluid state holder

77 Spring

78 Discharge hole

BEST MODE FOR CARRYING OUT THE INVENTION

(Embodiment 1)

FIG. 1 is a longitudinal sectional view of the compressor according to the first embodiment of the present invention, and FIG. 2 is a transverse sectional view of an expander section in the compressor according to the present embodiment. 1 and 2 show a rotary vane compressor and expander, but the compressor and expander are not limited to this. The rotary type, reciprocating type and scrolling type may be used. As the working fluid, a working fluid that expands from a supercritical phase to a liquid phase or a gas-liquid two phase, for example, a working fluid mainly composed of carbon dioxide is used.

In FIG. 1, the compressor according to the present embodiment includes a compressor unit 12, an electric motor unit 16, an expander unit 20, and a control unit inside a hermetic container 10. This control unit may be arranged inside or outside the closed container 10.

The compressor unit 12 includes a compression chamber 13, a drive shaft 14, and a rotor 15. By rotating the drive shaft 14 and the rotor 15, the working fluid sucked into the compression chamber 13 is changed from a low pressure to a high pressure. Compress. The electric motor section 16 includes a stator 17 and a rotor 18, and the rotor 18 is fixed to the drive shaft 14. The expander unit 20 includes a cylinder 21, a rotor 23, and a power recovery shaft 26 (hereinafter referred to as a shaft 26). The expander unit 20 sucks the working fluid through the suction path 32 and the suction hole 27, and the cylinder 21 and the rotor 23 A high pressure is expanded to a low pressure in the working chamber 25 as an expansion chamber to be formed, and the shaft 26 is rotated by discharging from the working chamber 25 through the discharge chamber 33 and the discharge passage 34. This rotational power is transmitted from the shaft 26 to the drive shaft 14 and is recovered as the driving force of the compressor section 12.

Further, in FIG. 2, the expander section 20 provided in the sealed container 10 includes a cylinder 21, a port 23, four vanes 24, a shaft 26, a canopy 31, a suction pipe. 35 and a solenoid valve 40.

That is, the cylinder 21 has a cylindrical inner wall 21a, and side plates 21b and 21c (see FIG. 1) are provided at both ends thereof. A cylindrical rotor 23 is disposed inside the cylinder 21, and a part of the outer periphery of the rotor 23 forms a small gap 22 with the inner wall 21 a of the cylinder 21. The inner wall 21 a and the outer periphery of the rotor 23 are in contact with each other at the base point (contact point) of the small gap 22.

The rotor 23 is provided with four grooves 23a perpendicular to the upper and lower end surfaces at a pitch of 90 deg. Each vane 24 is slidably inserted in each groove 23 a, and the tip of the vane 24 is in contact with the inner wall 21 a of the cylinder 21.

The working chamber 25 is formed as a space 25a, 25b, 25c, 25d, 25e surrounded by the inner wall 21a of the cylinder 21, the rotor 23 and the vanes 24! /. The shaft 26 is formed integrally with the rotor 23, and is rotatably supported by the side plates 21b and 21c. It is connected to 12 drive shafts 14.

In addition, the cylinder 21 is provided with a suction hole 27 through which the working fluid flows into the working chamber 25 and a discharge hole 28 through which the working chamber 25 force also flows out the working fluid. Further, the electromagnetic valve 40 that constitutes a part of the expander unit 20 in the sealed container 10 is disposed in the suction hole 27 immediately before the inlet of the working chamber 25 (that is, the expansion chamber).

In the vicinity of the discharge hole 28, there is provided an opening 28a that is opened in a range in the circumferential direction of the inner wall 21a of the cylinder 21. The range in which the opening 28a is provided is that if the number of vanes 24 is n, the base force of the small gap 22 is also at the start position 28b of {180 X (l + 1 / n)} deg in the rotational direction indicated by the arrow of the shaft 26. The range starts and ends at the end position 28c in the vicinity of the small gap 22. The starting position 28b of the opening 28a in FIG. 2 is a position of 225 deg because there are four vanes 24.

Also, a cover 31 is provided on the side of the cylinder 21, and a suction pipe 35 is inserted into the cover 31, and a suction path 32 that guides the working fluid to the suction hole 27 is formed inside the suction pipe 35. Yes. As shown in FIG. 1, a discharge chamber 33 for temporarily storing the working fluid flowing out from the discharge hole 28 is formed inside the sealed container 10, and inside the discharge pipe 36 joined to the sealed container 10, A discharge path 34 is formed through which the working fluid flows out from the discharge chamber 33.

[0012] Further, the configuration of the control unit will be described.

As shown in FIG. 1, the control unit includes a discharge pressure sensor 48, a suction temperature sensor 50, a discharge temperature sensor 51, a gap sensor 52, a solenoid valve control unit 60, and a working fluid state holding unit 61. Composed.

In other words, the solenoid valve 40 is energized via the solenoid valve control unit 60, and the solenoid valve 40 is electrically opened and closed to control the communication between the working chamber 25 and the suction hole 27. However, it is desirable that the solenoid valve 40 be normally opened and closed when energized (controlled), assuming an electrical problem. The reason for this is that if the solenoid valve is a normally open solenoid valve, it is easy to control the opening and closing of the valve (measure the timing of opening and closing), and it will not close even if an electrical problem occurs. This is because it does not function as an expander, which prevents the problem of non-expansion. The suction temperature sensor 50 measures the temperature of the working fluid in the suction path 32 or the suction hole 27 as the suction temperature Tb of the expander. Further, the discharge pressure sensor 48 and the discharge temperature sensor 51 measure the pressure and temperature of the working fluid in the discharge chamber 33 or the discharge path 34 as the discharge pressure Pc and the discharge temperature Tc of the expander. Any temperature sensor or pressure sensor may be used as long as it can measure the temperature and pressure of the working fluid. Also, the expander intake temperature Tb is measured between the condenser (see Fig. 11) and the intake pipe 35, and the expander discharge pressure Pc and the expander (see Fig. 11) are measured between the discharge pipe 36 and the evaporator (see Fig. 11). The discharge temperature Tc may be measured. The gap sensor 52 detects the rotation angle θ X of the shaft 14 using an angle detection gear 45 provided on the shaft 14.

Further, the solenoid valve control unit 60 controls the opening and closing of the solenoid valve 40. In addition, the working fluid state holding unit 61 holds data indicating the relationship between the volume and pressure of the working fluid when the working fluid expands in the working chamber 25, an approximate expression, and the like, and is configured using, for example, a semiconductor memory. Has been. The working fluid state holding unit 61 may be integrated with the solenoid valve control unit 60! / ヽ. Next, the operation of the expander unit in the compressor of the present embodiment configured as described above will be described first in the basic case where the solenoid valve 40 is normally open. FIG. 3 is a PV diagram of the working chamber when the solenoid valve in the present embodiment is normally open, that is, a PV diagram of the working chamber 25 of the expander section 20. In addition, description of the compressor part which is not related to the characteristic of this invention is abbreviate | omitted. The working chamber 25 is a space 25 a on the suction hole 27 side of the small gap 22. Thereafter, while the volume is increased with the rotation of the rotor 23, a process of sucking a working fluid having a suction pressure Pb corresponding to the high pressure Ph of the refrigeration cycle from the suction hole 27, that is, a suction process is performed. The inhalation process corresponds to AB in Fig. 3.

When the working chamber 25 reaches the position of the space 25b, the communication with the suction hole 27 is cut off to become a sealed space, and then the volume increases with the rotation of the rotor 23, and the pressure of the working fluid inside decreases. The process of going, that is, the expansion process is performed. The expansion process corresponds to BC in Fig. 3. The working chamber 25 has a maximum volume at the position of the space 25c. This time corresponds to C in Fig. 3, and the discharge pressure in the working chamber 25 is Pc. From the moment when the rotor 23 is slightly rotated from here, the working chamber 25 located in the space 25c communicates with the discharge hole 28 through the opening 28a, and the working fluid is pushed out from the working chamber 25 to the discharge chamber 33. Where the discharge pressure of the working chamber 25 in C When Pc is equal to the low pressure PI of the refrigeration cycle U, the reduced working fluid is discharged smoothly, and the volume of the working chamber 25 decreases at the low pressure P1. That is, the discharge process from C to D in Fig. 3 is performed.

Thereafter, the working chamber 25 communicates with the suction hole 27 again and returns to the state of A in FIG.

[0014] In practice, the low pressure P1 of the refrigeration cycle varies depending on the heat exchange conditions in the evaporator (see FIG. 11), the operating conditions of the refrigeration cycle, and the like. In the operation of the expander described above, the ratio of the volume at the moment when the working fluid is sealed (space 25b in FIG. 2) to the volume immediately before the working fluid is discharged (space 25c in FIG. 2), that is, the expansion ratio is constant. Therefore, when the low pressure P1 fluctuates, it cannot be made equal to the discharge pressure Pc of the expander. Therefore, in the present embodiment, the operation of changing the amount of working fluid sucked into the working chamber 25 using the electromagnetic valve 40 and controlling the discharge pressure Pc of the expander and the low pressure P1 of the refrigeration cycle to be equal is performed. Done.

Next, the opening / closing operation of the electromagnetic valve 40 will be described.

FIG. 4 shows the relationship between the opening / closing timing of the solenoid valve 40 in the present embodiment and the flow rate of the working fluid entering the working chamber 25 during the suction process. Here, the time from when the solenoid valve 40 is closed to open is expressed as time Top, and the time from when the solenoid valve 40 is opened to closed is expressed as time Tel.

First, the solenoid valve 40 is controlled to be opened immediately before the working chamber 25 communicates with the suction hole 27. If the solenoid valve 40 is kept closed at this time, the working chamber 25 is evacuated as it rotates, which causes a loss of braking the rotation of the rotor 23, which is not preferable. That is, the brake loss is minimized by a configuration having a control function in which the opening timing (that is, the time Top) at which the solenoid valve 40 is opened from the closed state is set to the suction start time at which the volume of the working chamber 25 is minimized. Can do.

Next, from time Top, the working chamber 25 communicates with the suction hole 27 and the working fluid is sucked into the working chamber 25. Then, the electromagnetic valve 40 is closed at a time Tel in which the working chamber 25 reaches the maximum volume Vb that can be sucked. As a result, the suction amount of the working fluid becomes a volume Vb ′ smaller than the maximum volume Vb. Thus, the magnitude of Vb ′ can be varied by changing the timing of the closing time Tel of the solenoid valve 40. In other words, with the configuration having a control function that sets the closing timing (that is, at the time of time Tel) for closing the solenoid valve 40 from the suction start time to the time when the volume of the working chamber 25 becomes the maximum, The amount of inhalation can be varied. On the other hand, a solenoid valve 40 is provided in the suction hole 27 just before the inlet of the working chamber 25, and the distance from the solenoid valve 40 to the inlet of the working chamber 25 of the suction hole 27 is shortened. The dead space in which the water cannot be recovered becomes smaller, and the reduction in expansion efficiency can be avoided.

[0016] Next, a method for determining the time Tel for closing the solenoid valve 40 will be described.

When considering an air conditioner that uses carbon dioxide as the working fluid, the efficiency of the refrigeration cycle and the high pressure Ph have a relationship that maximizes the efficiency at a certain high pressure. According to S. M. Liao, the high pressure that maximizes the refrigeration cycle efficiency (hereinafter referred to as the optimal pressure Popt) can be expressed by the following equation.

Popt = (2. 778-0. 0157 X te) tg + (0. 381 X te— 9. 34)… (Formula 1)

Here, te is the evaporator temperature (that is, the temperature corresponding to the discharge temperature Tc of the expander), tg is the condenser outlet temperature (that is, the temperature corresponding to the suction temperature Tb of the expander), and the respective temperatures are the discharge temperatures. It can be measured by the sensor 51 and the suction temperature sensor 50. Then, using Equation 1, a target expander suction pressure Popt can be calculated from the suction temperature Tb and the discharge temperature Tc.

Therefore, the refrigeration cycle is operated so that the high pressure Ph, that is, the suction pressure Pb of the expander corresponding to the high pressure Ph becomes the optimum pressure Popt as the target expander suction pressure. It is desirable because it maximizes.

[0017] Incidentally, since the working fluid of the present embodiment is in a gas-liquid two-phase state at the evaporator temperature te, the saturation pressure 'temperature of the working fluid is determined based on the evaporator temperature te. From this relationship, the low pressure P1 (evaporator pressure) of the refrigeration cycle, that is, the discharge pressure Pc of the expander corresponding to the low pressure P1 can be obtained. That is, even if the discharge pressure sensor 48 is not provided, a configuration in which the discharge temperature Tc measured by the discharge temperature sensor 51 is converted to obtain the expander discharge pressure Pc can be obtained, which leads to cost reduction.

Furthermore, the volume Vc of the working chamber 25 in the final state C (space 25c in FIG. 3) of the expansion process (curve BC in FIG. 3) is also known from the design specifications. Therefore, if the relationship between the volume of the working chamber 25 and the pressure is known, the target volume Vb of the expansion chamber that sucks the working fluid is determined by changing the state transition from the final state C to the initial state B of the expansion process. can do. For example, assuming that the working fluid is an ideal gas and the ideal isentropic change that does not cause leakage, friction, or heat in / out during the expansion process, the relationship between the volume of the working chamber 25 and the pressure is expressed by the following equation. The

PV ^K = (—Constant) · · · (Formula 2)

Where κ is the specific heat ratio.

By using Equation 2, in order to obtain the optimum pressure Popt with the suction pressure Pb as the target in the initial state B of the expansion process, the low pressure P1 in the final state C (that is, the detected discharge pressure Pc) From the chamber volume Vc (known from the design specifications), Vb expressed by the following equation is the target volume to be set for B, that is, the working fluid suction amount.

Vbo '= (Pl / Popt) ^{1 /} κVc

Then, using this Vbo ′, the timing of closing the electromagnetic valve 40 is determined. That is, the amount of working fluid introduced into the expansion chamber is determined by the expansion machine discharge pressure Pc (i.e., low pressure P1), suction temperature Tb, and discharge temperature Tc force. The time Tel will be determined so that the target amount obtained from

An example of the method for determining the time Tel from the target volume Vb is as follows. An angle detection gear 45 for detecting the rotation angle is installed on a part of the shaft 14. For example, as shown in FIG. 5, the angle detection gear 45 has a shape in which irregularities are regularly engraved in the circumferential direction, part of which is not concave, and a part 45a. Without the recess, the rotation angle θ X of the shaft 14 is detected by reading the unevenness of the angle detection gear 45 accompanying the rotation of the shaft 14 with the gap sensor 52 using the portion 45a as a rotation base. Since the relationship between the rotation angle Θb from the base point and the volume Vb of the working chamber 25 is known from the design specifications, the rotation angle Θbo from the base point to the point of the target volume Vb is obtained and the detected rotation The time when the angle Θ X reaches the rotation angle Θ bo is time Tel, and is the closing timing of the solenoid valve 40. By the way, in the actual expansion process BC, the relationship between the volume and pressure when the working fluid expands cannot be treated as an ideal gas expressed by Equation 2, for example, the expansion process for carbon dioxide Transition to a supercritical state force gas-liquid two-phase state. Also, the expansion process BC is not ideal isentropic change due to the effects of leakage, friction and fluid resistance. Therefore, in practice, the relationship between the volume and pressure of the working fluid in the expansion process is preferably expressed using experimental data or an approximate expression that also obtains experimental data force. Thus, obtaining the target volume Vb will result in higher operating efficiency compared to obtaining the target volume Vb.

The above-described working fluid state holding unit 61 holds data and approximate expressions representing the relationship between the volume and pressure of the above-described working fluid and the relationship between the saturation pressure and the temperature of the above-described working fluid. In other words, the working fluid state holding unit 61 that holds the relationship between the volume and pressure of the working fluid when expanding in the expansion chamber is provided, and the target volume Vb (that is, the target that maximizes the refrigeration cycle efficiency) is provided using this relationship. If it is the structure which calculates | requires (quantity), higher operating efficiency can be obtained.

[0019] As described above, in the present embodiment, the electromagnetic valve 40 is installed in the suction hole 27 in the sealed container 10 and immediately before the working chamber 25, and the low pressure P1 of the refrigeration cycle is detected. Operates by controlling the opening time (Tel Top) of the solenoid valve 40 with the solenoid valve controller 60 so that the high pressure Ph of the refrigeration cycle becomes the optimum pressure Popt that maximizes the refrigeration cycle efficiency based on P1 In other words, the flow rate of the working fluid entering the chamber 25 is adjusted. In other words, the volume of the expansion chamber in which the working fluid can be sucked by varying the opening and closing timing of the suction valve is the ideal volume, and the minimum dead space Therefore, even when the rotor 23 of the expander is directly connected to the drive shaft of the compressor, the operating conditions (constraints) of “density ratio = constant” can be eliminated, and the maximum power recovery is always possible, such as a high-pressure working fluid. To provide a compressor integrated with an expander Togashi.

The compressor of the present embodiment is used in a heat pump device to control the opening / closing timing of the intake valve of the compressor so that the amount of working fluid led to the expansion chamber becomes a target amount that maximizes the refrigeration cycle efficiency. As a result, the operation efficiency of the heat pump device can be constantly increased.

(Embodiment 2)

FIG. 6 is a longitudinal sectional view of the compressor according to the second embodiment of the present invention, and FIG. 7 is a transverse sectional view of the compressor shown in FIG. The compressor of the present embodiment shows the detailed shape of the rolling piston type expander section and the solenoid valve, and has a different configuration and operation from the first embodiment. I will explain the work. And the description regarding the same composition and the same operation is omitted.

The compressor according to the present embodiment includes a compressor unit 12, an electric motor unit 16, an expander unit 70, and a control unit inside the sealed container 10.

The expander unit 70 is fitted with a power recovery shaft 76 having an eccentric portion 76a (hereinafter referred to as shaft 76), a cylinder 71 having a cylindrical inner wall 71a, and the eccentric portion 76a. A rotor 73 that performs eccentric rotational movement inside the cylinder 71, and reciprocates inside the vane groove 71b of the cylinder 71 with its tip in contact with the rotor 73, and serves as an expansion chamber between the cylinder 71 and the rotor 73. A vane 74 that forms a working chamber 25 (space 25f, 25g), a spring 77 that is installed on the back of the vane 74 and presses the vane 74 against the rotor 73, and a side plate that supports the shaft 76 with the cylinder 71 interposed therebetween. The side plate 71c including 71c, 71d (see FIG. 6), the suction pipe 35, and the solenoid valve 40 is connected to the suction pipe 35, and the working fluid sucked from the suction pipe 35 is introduced into the working chamber 25. It has a suction hole 27. The side plate 71d has a discharge hole 78 for discharging the working fluid expanded in the working chamber 25 to the discharge chamber 33. The inlet of the working chamber 25 of the suction hole 27 and the outlet of the working chamber 25 of the discharge hole 78 are provided in the vicinity of the vane groove opening. In addition, as shown in FIG. 7, the electromagnetic valve 40 that is part of the expander unit 70 in the sealed container 10 includes a frame 80, a plunger 81, a core 82, a solenoid 83, and a spring 8. 4 and the like, and is arranged near the inlet of the working chamber 25 of the suction hole 27. The reason for this is that if the solenoid valve 40 is provided as close as possible to the inlet of the working chamber 25 of the suction hole 27, the distance between the working chamber 25 and the solenoid valve 40 is shortened, and refrigerant accumulates so that the expansion energy cannot be recovered. Dead space This is because a decrease in expansion efficiency can be avoided. When the motor unit 16 is energized to rotate the shaft 14 and the shaft 76, the rotor 73 performs an eccentric rotational motion, and the volume of the working chamber 25 changes. At this time, opening / closing control of the electromagnetic valve 40 is executed, and the working fluid is appropriately sucked into the working chamber 25 through the suction hole 27 and expanded in the working chamber 25. The expanded working fluid is discharged from the discharge hole 78. As described above, in the present embodiment, the electromagnetic valve 40 is installed in the airtight container 10 in the vicinity of the working chamber 25 of the suction hole 27, and the opening / closing timing of the electromagnetic valve 40 is varied to enter the working chamber 25. By adjusting the flow rate of the working fluid, the number of bypass lines can be reduced and the valve control In order to reduce the dead space on the intake side and eliminate the operating conditions (constraints) where the “density ratio = constant”, the maximum power recovery from the high-pressure working fluid can be achieved to always obtain high operating efficiency. Can do.

In addition, the rolling piston type expander part of the present embodiment has an advantage that the number of times of opening and closing the electromagnetic valve can be reduced as compared with the rotary vane type expander part of the first embodiment.

(Embodiment 3)

FIG. 8 is a longitudinal sectional view of the compressor according to the third embodiment of the present invention, and FIG. 9 is a transverse sectional view of an expander section in the compressor according to the present embodiment. 8 and 9 show rotary vane type compressors and expanders, but the compressor and expander types are not limited to this, and other types such as rotary type, reciprocating type, scroll type, etc. But you can. As the working fluid, a working fluid that expands from a liquid phase or a supercritical phase to a gas-liquid two phase, or a working fluid mainly composed of carbon dioxide is used.

In FIG. 8, the compressor of the present embodiment is configured to include a compressor unit 12, an electric motor unit 16, and an expander unit 20 inside the hermetic container 10. The compressor unit 12 includes a compression chamber 13, a drive shaft 14, and a rotor 15, and compresses the working fluid sucked into the compression chamber 13 from a low pressure to a high pressure by rotating the drive shaft 14 and the rotor 15. . The electric motor unit 16 includes a stator 17 and a rotor 18, and the rotor 18 is fixed to the drive shaft 14. The expander unit 20 includes a cylinder 21, a rotor 23, and a shaft 26, and sucks the working fluid through the suction passage 32 and the suction hole 27, and is high in the working chamber 25 formed by the cylinder 21 and the rotor 23. The pressure is also expanded to a low pressure and discharged from the working chamber 25 through the discharge chamber 33 and the discharge path 34, thereby obtaining rotational power for the shaft 26. This rotational power is transmitted from the shaft 26 to the drive shaft 14 and is recovered as the drive force of the compressor unit 12.

[0023] Further, the configuration of the expander unit will be described in detail.

As shown in FIG. 9, the expander 咅 20 has a cylinder 21, a rotor 23, four vanes 24, a shaft 26, a valve mechanism 30, a cover 31, a suction pipe 35, an electromagnetic That is, the cylinder 21 includes a cylindrical inner wall 21a, and side plates 21b and 21c (see FIG. 8) at both ends thereof. Is provided. A cylindrical rotor 23 is disposed inside the cylinder 21, and a part of the outer periphery of the rotor 23 forms a small gap 22 with the inner wall 21 a of the cylinder 21. The inner wall 21 a and the outer periphery of the rotor 23 are in contact with each other at the base point (contact point) of the small gap 22.

The working chamber 25 is formed as a space 25a, 25b, 25c, 25d, 25e surrounded by the inner wall 21a of the cylinder 21, the rotor 23 and the vanes 24! /. The shaft 26 is formed integrally with the rotor 23, is rotatably supported on the side plates 21b and 21c, and is connected to the drive shaft 14 of the compressor unit 12.

The electromagnetic valve 40 that is part of the expander unit 20 in the sealed container 10 is disposed at a position close to the working chamber 25 of the suction hole 27. By providing the solenoid valve 40 at a position close to the working chamber 25, the distance between the working chamber 25 and the solenoid valve 40 is shortened, the dead space is reduced, and the reduction of the expansion efficiency is avoided.

Further, the cylinder 21 has a suction hole 27 through which the working fluid flows into the working chamber 25, a first discharge hole 28 (hereinafter referred to as a discharge hole 28) and a second discharge hole 29 through which the working chamber 25 force working fluid flows out. (Hereinafter, the discharge hole 29) is provided. Then, when the number of vanes 24 is n, the discharge hole 28 is moved to a position where the base force of the small gap 22 has moved by an angle of {180 X (1 + 1 / n)} deg in the rotation direction indicated by the arrow of the shaft 26. Is provided. In the present embodiment, since there are four vanes 24, the position is 225deg. Further, the discharge hole 28 is provided with a valve mechanism 30 including a discharge valve lead valve 30a and a valve stop 30b.

On the other hand, the discharge hole 29 is provided in the vicinity of the base point of the small gap 22, and a part of the discharge hole 29 has a shape including the position of the base point of the small gap 22 at a position of 315 deg in the rotation direction of the shaft 26. No valve mechanism is provided. The position of the discharge hole 29 is not limited to this. If the center angle around the shaft 26 of the inner wall 21a of the cylinder 21 between the suction hole 27 and the discharge hole 29 is n vanes 24 (360Zn) or less As long as the discharge hole 29 is in the vicinity of the base point of the small gap 22.

In addition, a cover 31 is provided on the side of the cylinder 21, and the suction pipe 35 is provided on the cover 31. Is inserted, and a suction passage 32 for guiding the working fluid to the suction hole 27 is formed in the suction pipe 35. As shown in FIG. 8, a discharge chamber 33 for storing and storing the working fluid flowing out from the discharge holes 28 and 29 is formed inside the sealed container 10, and the discharge pipe 36 joined to the sealed container 10 is provided. Inside, a discharge path 34 is formed for allowing the working fluid to flow out from the discharge chamber 33 to the outside.

Further, the solenoid valve 40 is energized through a wiring (not shown) from a control device (not shown), and the solenoid valve 40 is electrically opened and closed, whereby communication between the suction hole 27 and the suction path 32 is established. It is configured to control. In addition, it is desirable that the solenoid valve 40 be normally opened and closed when energized (controlled), assuming an electrical problem. The reason for this is that if an electromagnetic valve is used, it is easy to control the opening and closing of the valve (timing the opening and closing timing), and since it is a normally open solenoid valve that does not close even with an electrical trouble, the expander As a result, the non-inflating harmful effect of not functioning as a non-function is prevented.

Next, the operation of the expander unit in the compressor of the present embodiment configured as described above will be described with reference to FIGS. 9 and 3 in the case where the solenoid valve 40 is normally open. FIG. 3 is a PV diagram of the working chamber when the solenoid valve is normally open in the present embodiment, that is, a PV diagram of the working chamber 25 of the expansion unit 20. Note that the description of the compressor section not related to the features of the present invention is omitted.

The working chamber 25 is generated in a space 25 a on the suction hole 27 side of the small gap 22. Thereafter, the process of sucking the working fluid having the high-pressure side pressure Pb from the suction hole 27, that is, the suction process is performed while increasing the volume as the rotor 23 rotates. The inhalation process corresponds to AB in Figure 3.

When the working chamber 25 reaches the position of the space 25b, the communication with the suction hole 27 is cut off to become a sealed space, and then the volume increases with the rotation of the rotor 23, and the pressure of the working fluid inside decreases. The process of going, that is, the expansion process is performed. The expansion process corresponds to BC in Fig. 3. The working chamber 25 has a maximum volume at the position of the space 25c. This time corresponds to C in Fig. 3, and the pressure in the working chamber 25 is Pc. Then, at the moment when the rotor 23 is slightly rotated, the working chamber 25 positioned in the space 25 c communicates with the discharge hole 28. Here, when the reed valve 30a is not provided in the discharge hole 28 and the pressure Pc is equal to the pressure in the discharge chamber 33, the working fluid is pushed out from the working chamber 25 to the discharge chamber 33 and operates in the state of the pressure Pc. Working chamber while pushing out fluid 25 The volume of is decreasing. That is, the discharge process in which the C force in Fig. 3 also shifts to D is performed.

Next, the case where the solenoid valve 40 is controlled to open and close will be described.

FIG. 4 shows the relationship between the opening / closing timing of the electromagnetic valve 40 in the present embodiment and the flow rate of the working fluid entering the working chamber 25 during the suction process. Here, the time from when the solenoid valve 40 is closed to open is expressed as time Top, and the time from when the solenoid valve 40 is opened to closed is expressed as time Tel.

Next, from time Top, the working chamber 25 communicates with the suction hole 27 and the working fluid is sucked into the working chamber 25. Then, the solenoid valve 40 is closed at the time Tel that the working chamber 25 reaches the maximum volume Vb that can be sucked. As a result, the amount of working fluid drawn becomes V, which is smaller than Vb. Thus, the magnitude of Vb ′ can be varied by changing the timing of the closing time Tel of the solenoid valve 40. In other words, the expansion chamber has a control function in which the closing timing for opening the solenoid valve 40 from opening to closing (that is, at the time of time Tel) is the time from the suction start time until the volume of the working chamber 25 becomes maximum. The flow rate of the working fluid entering can be varied.

[0027] The operation when the time Tel is changed will be described with reference to the PV diagram of the working chamber when the opening / closing timing of the solenoid valve in the present embodiment in FIG. 10 is changed.

The working chamber 25 performs a suction process in which the working fluid of the pressure Pb on the high pressure side is sucked from the suction hole 27 until the state force of the space 25a in FIG. 9 also closes the electromagnetic valve 40. In other words, the inhalation process corresponds to that of Fig. 10. And the amount of inhalation at this time is Vb '.

When the solenoid valve 40 is closed at time Tel, the volume increases with the rotor 23, and the pressure of the internal working fluid decreases to perform the expansion process. This process corresponds to B'H in Figure 10.

The working chamber 25 has a maximum volume at the position of the space 25c. At this time, the pressure in the working chamber 25 is P lower than the pressure Pc when the solenoid valve 40 is normally opened. . This process corresponds to HC in Fig. 10.

Then, the discharge of the working fluid is started at the moment when the rotor 23 rotates slightly and the working chamber 25 communicates with the discharge hole 28.

Here, when the reed valve 30a is not provided in the discharge hole 28, for example, when the solenoid valve 40 is shifted from a normally open state to a state in which the above opening / closing control is performed, the discharge chamber 33 of the pressure Pc is changed to the working chamber 25. The working fluid flows backward, and the pressure in the working chamber 25 rises from PcT to Pc with the volume kept constant at Vc. That is, from FIG. 10 to C, an overexpansion loss occurs in which the power of the area of the part surrounded by CC'H becomes a loss.

However, in this embodiment, the reed valve 30a is provided in the discharge hole 28, and the reed valve 30a closes the discharge hole 28 by the pressure difference between the pressure PcT of the discharge chamber 33 and the pressure Pc of the working chamber 25. Therefore, the working fluid can be prevented from flowing from the discharge chamber 33 into the working chamber 25. Thereafter, the volume of the working chamber 25 decreases with the rotation of the rotor 3, but since it remains closed by the discharge hole 28 force S reed valve 30a, compression occurs in the space 25c, and the pressure is again in FIG. Ascend C'B '.

The reed valve 30a is opened for the first time at the moment when the pressure in the working chamber 25 exceeds Pc, that is, at H in FIG. 10 when the pressure in the working chamber 25 reaches a predetermined value. This process corresponding to H is called the recompression process. Since the discharge valve is the reed valve 30a, there is an advantage that when the pressure in the working chamber 25 reaches a predetermined value, it automatically opens and recompression is performed.

Thereafter, as the rotor 23 rotates, the working chamber 25 reduces the volume while discharging the working fluid having the low-pressure side pressure Pc from the discharge hole 28, that is, a discharge process.

During this discharge process, the force that eliminates the communication with the discharge hole 28 while the working chamber 25 moves from the space 25d to the position of the space 25e causes a part of the discharge hole 29 to rotate from the base point of the small gap 22 to the rotation direction of the shaft 26. If the number of vanes is 315 deg, that is, the number of vanes is n, the shape includes the position moved in the circumferential direction by (360 Zn) deg, which is the pitch of the vanes 24 from the discharge holes 28. Continue from hole 29. This discharge process corresponds to HD in Fig. 10.

[0029] Next, an example of time-telling change control for closing the solenoid valve 40 will be described. For example, in a heat pump system, the discharge pressure of the working fluid discharged from the compressor is measured by, for example, a pressure sensor, and the target discharge efficiency and the efficiency of the entire system including the compressor and expander are the best. The time width from time Top to time Tc is controlled by comparing the pressure with the discharge pressure of the compressor and the target pressure. In other words, when the discharge pressure of the compressor is higher than the target pressure, the flow rate of the working fluid is increased by increasing the time width of the difference between the time Top and the time Tel. In addition, when the discharge pressure of the compressor is smaller than the target pressure, the time width of the time Top and the time Tel is reduced to reduce the flow rate of the working fluid. As a result, the efficiency of the entire system can be maximized.

That is, by using the compressor of the present embodiment for a heat pump device and changing the opening / closing timing of the suction valve to control the flow rate of the working fluid entering the expansion chamber, the operating efficiency of the heat pump device is always high. Can be.

The target pressure is a value that can determine the physical property value of the working fluid.

In addition, changing the intake valve opening / closing timing, that is, controlling the time width, for example, detects the rotation speed of the expander and the rotation angle from the base point, and based on this rotation speed and rotation angle! This can be done with a configuration (not shown) that opens and closes the solenoid valve 40 by setting the inhalation start time (time point) and time span.

As described above, in the present embodiment, the solenoid valve 40 is installed in the sealed container 10 at a position close to the working chamber 25 of the suction hole 27 and the time width (Tel Top) during which the solenoid valve 40 is open is controlled. As a result, the flow rate of the working fluid entering the working chamber 25 is adjusted and the dead space is reduced. Therefore, even when the rotor 23 of the expander is directly connected to the drive shaft of the compressor, the operation of “density ratio = constant” is performed. It is possible to provide an expander-integrated compressor that can eliminate the conditions (constraints) and always recover power from the high-pressure working fluid to the maximum extent possible.

In the present embodiment, since the discharge hole 28 is provided with the valve mechanism 30 including the reed valve 30a and the valve stop 30b, the discharge chamber 33 can be used in the case of overexpansion that can occur when the electromagnetic valve 40 is controlled. The working fluid is prevented from flowing back into the working chamber 25 and can be recompressed to the discharge pressure Pc, so there is no overexpansion loss (corresponding to the area of CC'H in Fig. 10)! A machine-integrated compressor can be provided.

The valve mechanism 30 described in the third embodiment is applied to the discharge hole 78 in the second embodiment. I'll do it for you.

Industrial applicability

The compressor according to the present invention and the heat pump device using the compressor control the expansion chamber volume of the expander into which the working fluid is sucked by opening and closing a suction valve installed in the suction hole immediately before the inlet of the expansion chamber, Since high-pressure working fluid force also recovers power to the maximum, high operation efficiency can be obtained at all times, and it can be applied to an expander-integrated compressor, a heat pump device using the compressor, an air conditioner, and the like.

Claims

The scope of the claims

[1] A compressor section having a compression chamber and a drive shaft, and compressing the working fluid sucked into the compression chamber by rotating the drive shaft;

An expansion chamber, a suction hole for guiding the working fluid to the expansion chamber with an expander suction pressure, a discharge hole for discharging the working fluid from the expansion chamber, and a power recovery shaft connected to the drive shaft

An expander unit that obtains rotational power of the power recovery shaft by expanding the working fluid sucked into the expansion chamber;

A sealed container in which the compressor unit and the expander unit are disposed;

A fluid machine comprising: a suction valve for controlling an amount of working fluid guided to the expansion chamber in the sealed container.

[2] pressure detecting means for detecting the expander discharge pressure of the working fluid discharged from the discharge hole;

The opening / closing timing of the intake valve is adjusted so that the amount of working fluid guided from the suction hole to the expansion chamber becomes a target amount obtained from the expander suction pressure and the expander discharge pressure that maximize the refrigeration cycle efficiency. The fluid machine according to claim 1, further comprising: an opening / closing timing control means for controlling

[3] A suction temperature sensor that measures a suction temperature of the working fluid sucked into the suction hole, and a discharge temperature sensor that measures a discharge temperature of the working fluid discharged from the discharge hole, and the suction temperature and the The fluid machine according to claim 2, wherein the expander suction pressure is obtained from a discharge temperature.

[4] A discharge temperature sensor for measuring the discharge temperature of the working fluid discharged from the discharge hole is provided,

The discharge temperature force is obtained from the expander discharge pressure, and the suction hole force is determined from the expander suction pressure that maximizes the refrigeration cycle efficiency and the expander discharge pressure. An opening / closing timing control means for controlling the opening / closing timing of the intake valve so as to achieve a target amount;

The fluid machine according to claim 1, further comprising:

5. The fluid machine according to claim 1, wherein the suction valve is a solenoid valve.

[6] The opening timing at which the suction valve is opened from the closed time is defined as the suction start time at which the volume of the expansion chamber is minimized, and the closing timing at which the suction valve is opened from the closed time is expanded from the suction start time. 2. The fluid machine according to claim 1, wherein the fluid machine is configured to have a control function of setting a time until the volume of the chamber reaches a volume corresponding to a target amount.

[7] A working fluid state holding unit is provided that holds a relationship between the volume and pressure of the working fluid when expanding in the expansion chamber, and the relationship between the volume and pressure of the working fluid held by the working fluid state holding unit is provided. The fluid machine according to claim 1, wherein the target amount is obtained by using the fluid machine.

8. The fluid machine according to claim 1, wherein the fluid machine is operated using a working fluid that expands from a supercritical phase to a liquid phase or a gas-liquid two phase.

9. The fluid machine according to claim 1, wherein the fluid machine is operated using a working fluid mainly composed of carbon dioxide.

10. The fluid machine according to claim 1, wherein a discharge valve is provided in a discharge hole of the expander.

11. The fluid machine according to claim 10, wherein the discharge valve is a reed valve, and the discharge valve opens when the pressure in the expansion chamber reaches a predetermined value.

12. A heat pump apparatus using the fluid machine according to claim 1, wherein the amount of working fluid led to the expansion chamber is controlled by controlling the opening / closing timing of the suction valve so that the refrigeration cycle efficiency is maximized. A heat pump device characterized in that the quantity is a quantity.