KR20030064637A - Positive displacement machine - Google Patents

Abstract

It aims at simplifying the valve mechanism in the volumetric machine, improving the reliability of the high pressure working fluid, and reducing the mechanical friction loss.

A volumetric machine having a reciprocating member (1) which performs a swinging motion in conjunction with a reciprocating motion. The conduction between the operating chamber and the suction pressure space or the discharge pressure space is switched using the swinging motion. In addition, with the above-mentioned volumetric machine, only the piston diameter is made relatively small with respect to the size of each sliding part.

By improving the productivity and reliability of the volumetric machine, a compressor that can withstand use in ultra-high pressure refrigerants such as carbon dioxide can be put to practical use, and the efficiency of the entire system such as a refrigeration cycle is also improved.

Description

Volumetric Machines {POSITIVE DISPLACEMENT MACHINE}

TECHNICAL FIELD This invention relates to the efficiency improvement technique of a refrigeration air conditioner, a fuel cell system, etc. using a volumetric machine and a volumetric machine.

In the conventional reciprocating volumetric machine, as in the compressor described in Fig. 7 of JP-A-9-72275, in order to alternately communicate the suction chamber space or the discharge chamber space with the increase or decrease of the volume, The valve mechanism comprised of movable parts was used.

Moreover, the reciprocating member in the compressor of FIG. 7 of Unexamined-Japanese-Patent No. 9-72275 was formed by inserting an arm part in the center of a piston part.

In the above prior art, there are many moving parts constituting the reciprocating displacement type machine, which causes a problem of lowering productivity and reliability. It is a first object of the present invention to provide a reciprocating volumetric machine having a small number of parts and high reliability.

Moreover, in the said prior art, it is difficult to reduce the diameter of a piston part or to enlarge the ratio of the diameter of an arm part with respect to the diameter by the restriction | limiting from assembly property, and the sliding which arises in the arm part which is a sliding part by the pressure of a working fluid is difficult. There was a limit to the reduction of the moving load and the sliding surface pressure. For this reason, there exists a problem that the increase of a mechanical friction loss and the fall of the reliability of a sliding part are easy to produce especially when a working fluid is high pressure. It is a second object of the present invention to provide a reciprocating volumetric machine having high reliability of sliding parts due to low mechanical friction loss even when the working fluid is high pressure.

Moreover, in the system using the volumetric machine which applies the high pressure working fluid, since the energy stored in the high pressure working fluid is lost by the flow path resistance loss, such as a throttle mechanism, there existed a problem that it was wasted from a viewpoint of energy efficiency. The third object of the present invention is to recover energy when expanding the high-pressure working fluid with a system using a volumetric machine to reduce the pressure, and also to reduce the energy loss such as mechanical friction loss generated during the recovery operation, thereby improving efficiency. To provide a system.

1 is an overall side sectional view of a pump as a first embodiment of the present invention;

FIG. 2 is a sectional view taken along the line A-A in FIG. 1; FIG.

3 is a cross-sectional view taken along line B-B in FIG. 1;

4 is a sectional view taken along the line C-C in FIG.

Fig. 5 is a sectional view taken along the line D-D in Fig. 1;

Figure 6 is a side cross-sectional view of the inflator as a second embodiment of the present invention.

Fig. 7 is a sectional view taken along the line E-E in Fig. 6;

Fig. 8 is a sectional view taken along the line F-F in Fig. 6;

FIG. 9 is a sectional view taken along the line G-G in FIG. 6; FIG.

10 is a sectional view taken along the line H-H in FIG.

Fig. 11 is a side sectional view of the entirety of the expansion and the compressor using the refrigerant as the working fluid of the third embodiment of the present invention;

12 is a configuration of a refrigeration cycle when the expansion and the compressor, which is a third embodiment of the present invention, is applied to a refrigeration and air conditioner.

Figure 13 is a side cross-sectional view of the entirety of an inflation and compressor for a fourth embodiment of the present invention.

FIG. 14 is a sectional view taken along the line I-I in FIG. 13; FIG.

FIG. 15 is a cross-sectional view taken along the line J-J in FIG. 13; FIG.

FIG. 16 is a cross-sectional view taken along line K-K in FIG. 13; FIG.

Fig. 17 is a system configuration diagram when the expansion and compressor as the fourth embodiment of the present invention is applied to a fuel cell system.

18 is an overall side sectional view of a compressor as a fifth embodiment of the present invention;

<Description of the code for the main part>

1, 21, 45, 66: reciprocating member

1a, 21a, 21c, 45a, 45c, 66a: piston head part

1b, 21d, 45d, 66b: arm part

1c, 21e, 66c: pin

1d, 21f, 45f: contact passage

2, 16, 22, 48, 69: cylinder block

2a, 16a, 22a, 22b, 69a: inner cylindrical surface

2b, 16b, 21b, 22c, 45b, 48d, 66f: suction port

2c, 16c, 22d, 23a, 48e, 74a: discharge port

3: spherical bush

4, 33, 50, 67: drive shaft

4a, 33a, 67a: driving arm part

4b, 13, 19b, 33b, 55, 67b, 82: balanced mass

5, 42, 68: bearing frame

5a, 68a: bearing part

6, 23, 54, 74: cylinder head

7, 24, 40, 41, 65: operating room

8, 9, 17: cover

10, 18, 27, 47, 53, 70: suction piping

11, 32, 49, 79: discharge pipe

12, 34, 80: driving motor

12a, 20a, 34a, 80a: stator part

12b, 20b, 34b, 80b: rotor part

14, 81: motor cover

15, 46: elliptic trajectory

19: output shaft

19a: output arm

20: oscillator

25, 73: suction valve plate

26, 72 rivet

28, 75: discharge valve plate

29, 76: press the discharge valve

30, 77: discharge space

31, 78: discharge chamber cover

35, 56: expansion and compressor

36: cycle piping

37: condenser

38: evaporator

39 expansion means

43: ball bearing

44: needle bearing

45e: Nut

45g, 66d: inlet

45h, 52, 66e, 71: interior space

48c, 48g: suction passage

48f: discharge passage

51: motor

57: air

58: air cleaner

59: compressed air

60: Fuel Cell Stack

60a: cathode portion

60b: anode part

60c: ion permeable membrane

60d: power

61: fuel gas

62: exhaust gas

63: high pressure exhaust air

64: low pressure exhaust air

In order to achieve the first object, a reciprocating member having a piston portion for changing the volume of the working space enclosed by the reciprocating motion and two arm portions extending opposite to each other in a direction perpendicular to the reciprocating direction of the piston portion; A guide member which is a part of the working space and guides the reciprocating motion of the piston portion, and two shaft members which rotate in the opposite directions with the same axial direction, and support the arm portions at positions radially offset from the rotation axis thereof, respectively. In a volumetric machine in which a piston portion reciprocates while oscillating around an axis in the reciprocating direction, the working fluid is used in accordance with the volume increase and decrease of the working space by using the above-described movement of the reciprocating member without using the movable part for the valve mechanism. Space, for example, suction chamber space or discharge chamber space, and the operating space It will configure a communication path for.

Moreover, in order to achieve the said 2nd objective, the reciprocating member which has a piston part which changes the volume of the operation space enclosed by the reciprocating motion, and two arm parts which extend to the opposite sides in the direction orthogonal to the reciprocating direction of the piston part, And a guide member that is part of the working space and guides the reciprocating motion of the piston portion, and two shaft members each supporting the arm portion at a position axially equal to each other and rotating radially from the rotation axis. In a volume machine in which a piston portion reciprocates while oscillating around an axis in the reciprocating direction, the reciprocating member is formed by inserting a member having a piston portion in the center of a member having two arm portions.

Moreover, in order to achieve the said 3rd objective, the reciprocating member which has a piston part which changes the volume of the operating space enclosed by the reciprocating motion, and two arm parts which extend to the opposite sides in the direction orthogonal to the reciprocating direction of the piston part, And a guide member that is part of the working space and guides the reciprocating motion of the piston portion, and two shaft members each supporting the arm portion at a position axially equal to each other and rotating radially from the rotation axis. The piston unit is a system having a volumetric machine that reciprocates while oscillating around an axis in the reciprocating direction as one component, and has a system having a compression stroke and an expansion stroke. For example, at least one of the two operating chambers operated by the piston units provided at both ends of the reciprocating member is composed of a compression chamber and the other of the expansion chamber, and powered by a compression chamber to supply at least a high pressure of the working fluid. A volumetric machine that reduces a pressure while guiding a part to the expansion chamber to recover power is used as a component, and in a refrigeration air conditioner system, a compression stroke and an expansion stroke of a refrigeration cycle are performed.

Hereinafter, each embodiment of the present invention will be described with reference to Figs. First, the first embodiment will be described with reference to Figs. 1 to 5 show a volumetric pump which is a first embodiment of the present invention.

The reciprocating member 1 is guided by its two inner circumferential cylindrical surfaces 2a of the cylinder block 2 respectively to guide the two piston heads 1a to perform reciprocating motion and rotation about the reciprocating direction axis. Is supported. Two cylindrical arm portions 1b protruding from each other in the direction perpendicular to the reciprocating direction are inserted into the piston head portion 1a of the reciprocating member 1, and are fixed by the pins 1c.

Two arm parts 1b are rotatably inserted in the inner circumferential cylindrical surface of the spherical bush 3, respectively. The outer circumferential spherical portions of the two spherical bushes 3 are respectively supported by spherical treatment at positions which are radially offset from the rotation axis of the drive shaft 4 by the drive arm portions 4a of the drive shaft 4.

As a result, the two arm portions 1b and the two drive shafts 4 of the reciprocating member are connected at positions deviated from the rotation shaft of the drive shaft 4 in a state where relative rotation and relative inclination direction changes are possible. A balance mass 4b is formed on the opposite side in the radial direction of the drive arm portion 4a of the drive shaft 4. In addition, the two drive shafts 4 are rotatably supported by the bearing portions 5a of the bearing frame 5, respectively. The two bearing frames 5 are fixed to the cylinder block 2 by bolts so that the central axes of their bearing portions 5a are arranged on the same axis with each other.

The central axes of the two inner circumferential cylindrical surfaces 2a formed in the cylinder block 2 are similarly coaxial with each other, and the central portions of the bearing portions of the bearing frame 5 fixed to the cylinder block 2 are perpendicular to each other.

The two opening ends of the inner circumferential cylindrical surface 2a formed in the cylinder block 2 are closed by the cylinder head 6 fixed with bolts, respectively, and the piston head portion 1a of the reciprocating member and the inner circumference of the cylinder block. Two operating chambers 7 surrounded by the cylindrical surface 2a and the cylinder head 6 are provided. The piston head portion 1a of the reciprocating member is provided with a communication passage 1d to the operating chamber 7, and the communication passage 1d has two openings in the cylindrical surface of the piston side surface. The cylinder block 2 is provided with the suction port 2b and the discharge port 2c which respectively open in the inner peripheral cylindrical surface 2a, and each opening part opposite the inner peripheral cylindrical surface 2a is provided in the cylinder block 2, respectively. It is closed by the cover 8 and the cover 9 which were fixed by the bolt etc. (not shown). A suction pipe 10 inserted from the outside of the pump is connected to the cover 8 that closes the opening of the suction port 2b, and a cover 9 which closes the opening of the discharge port 2c is inserted from the outside of the pump. The discharge pipe 11 is connected.

Stator portions 12a of the driving motor 12 are fixed to the two bearing frames 5 by bolts, and driving arm portions (2) are provided on the two driving shafts 4 with the bearing portions 5a interposed therebetween. The rotor part 12b of the drive motor 12 is being fixed to the opposite side to 4a). The rotor portion 12b is attached with a balance mass 13 which generates smaller centrifugal force in the opposite direction to the balance mass 4b described above. The two drive motors 12 constituted of the stator part 12a and the rotor part 12b are the same, but are assembled in opposite postures in the overall configuration of the displacement pump, and the two drive shafts 4 Rotate in reverse direction to each other. In the first embodiment, the driving motor 12 on the right side and the driving motor 12 on the left side in Fig. 1 are configured to rotate in clockwise and counterclockwise directions, respectively, as viewed from the right side of the drawing. have. In addition, the motor cover 14 is fixed to the two bearing frames 5 by simultaneous fastening by the fixing bolt to the cylinder block 2.

In the above configuration, when the two drive shafts 4 are driven to rotate in opposite directions to each other, the centers of the two spherical bushes 3 at positions radially offset from the rotation shafts of the drive shafts 4 in the vertical direction in FIG. Reciprocates in the same phase and reciprocates in phases opposite to each other in the ground vertical direction of FIG. 1, so that the two cylindrical arm portions 1b are supported by the spherical bush 3 ), As described in Japanese Patent Laid-Open No. 9-72275 (Fig. 8), repeats the swing around the reciprocating direction axis while reciprocating. At this time, the piston side opening of the communication passage 1d formed in the piston head portion 1a of the reciprocating member 1 is doubled with respect to the amount of deviation between the center of the spherical bush 3 and the rotational axis of the drive shaft 4. The stroke of the swinging motion is reduced in the ratio of dividing the piston outer diameter by the distance between the centers of the two spherical bushes 3 in the swinging direction. That is, the movement to draw the elliptic trajectory 15 is performed when viewed from the rotation axis direction of the drive shaft 4.

2 to 5, the positions of the suction port 2b or the discharge port 2c are described in the respective cross sections, and the above described communication channel 1d of the piston head portion 1a in the position opposite to them is shown. The opening position is shown by the broken line, and the elliptic trajectory 15 is shown by the dashed-dotted line. In addition, the direction of movement of the opening of the communication passage 1d when each drive shaft 4 rotates in the direction is indicated by an arrow. The positional relationship between the opening of the communication passage 1d and the elliptical trajectory 15 and the discharge port 2c in FIG. 2 is then changed at a time when the volume of the upper operating chamber 7 in FIG. 1 changes from decreasing to increasing. It has shown that the conduction state of the discharge port 2c and the operation chamber 7 by the communication passage 1d up to is cut off. The positional relationship between the opening of the communication passage 1d, the elliptic trajectory 15, and the suction port 2b in Fig. 3 is a communication passage in the future when the volume of the upper operating chamber 7 changes from decreasing to increasing. (1d) shows that the conduction state between the suction port 2b and the operation chamber 7 is secured. The positional relationship between the opening of the communication passage 1d, the elliptic trajectory 15, and the suction port 2b in FIG. 4 is then changed at a time when the volume of the lower operating chamber 7 in FIG. 1 changes from increasing to decreasing. It shows that the conduction state between the suction port 2b and the operation chamber 7 by the communication passage 1d up to is blocked.

The positional relationship between the opening of the communication passage 1d, the elliptic trajectory 15, and the discharge port 2c in FIG. 5 is a communication passage in the future when the volume of the lower operation chamber 7 changes from increasing to decreasing. (1d) shows that the conduction state between the discharge port 2c and the operation chamber 7 is secured. In the first embodiment, the low pressure working fluid (liquid) is supplied through the suction pipe 10 to make the suction port 2b a low pressure working fluid space, and the discharge port 2c is a high pressure working fluid space. As a result, the pressurized working fluid (liquid) is discharged from the discharge pipe 11.

As described above, according to the first embodiment, the low-pressure working fluid space is communicated with the low-pressure working fluid space in a period where the volume of the working chamber space is increasing, and the high-pressure working fluid space in the period where the volume of the working space is decreasing. Communication between the operating chamber and the operation chamber can be realized without using a movable part for the valve mechanism. Therefore, there is an effect that a reciprocating volumetric pump having a small number of parts and high productivity and reliability can be provided. Moreover, for the reason described in Japanese Patent Laid-Open No. 9-72275, it is also possible to reduce the excitation force due to the fluctuation of the drive torque and the inertia force of the reciprocating mass while being a reciprocating displacement pump.

In addition, in the first embodiment, the high pressure working liquid is supplied to the suction port 2b via the suction pipe 10, and the pressure reducing working liquid is discharged from the discharge port 2c via the discharge pipe 11. By changing, the hydraulic motor having the features and effects similar to those of the first embodiment can be obtained by using the two drive shafts 4 as output shafts. At that time, if two oscillators represented by the drive motor 12 are driven with their output shafts and given the same load to each other, the reciprocating volume type hydraulic pressure is similarly applied for the reason described in Japanese Patent Laid-Open No. 9-72275. In spite of being a motor, it is possible to make the excitation force due to the fluctuation of the drive torque and the inertial force of the reciprocating mass very small.

Next, a second embodiment of the present invention will be described with reference to Figs. 6 to 10 show a volume expander as a second embodiment of the present invention. Since the configuration of each component is substantially the same as that of the first embodiment of Figs. 1 to 5, the difference between them will be described. The cylinder block 16 is provided with the suction port 16b and the discharge port 16c which open to the inner peripheral cylindrical surface 16a, respectively, but the suction port 16b is smaller than the discharge port 16c. In addition, a high pressure working fluid (gas) is supplied through a suction pipe 18 connected to the cover 17 to make the suction port 16b a high pressure working fluid space, and the discharge port 16c a low pressure working fluid space. This configuration is for discharging the working fluid (gas) reduced in pressure than the discharge pipe 11. According to the above configuration, the operating chamber 7 conducts the high pressure working fluid (gas) through the contact port 1d of the piston head portion 1a through the communication passage 1d of the piston head portion 1a only during the initial period of the suction stroke in which the volume thereof increases. In the later period of the intake stroke, it becomes a sealed space that is blocked from both the intake and discharge ports to increase the volume and expand the working fluid (gas) therein. The discharge port 16c is sufficiently large, and the operating chamber 7 conducts with the discharge port 16c via the communication passage 1d of the piston head portion 1a and expands in the entire period of the discharge stroke whose volume is reduced. To discharge the low pressure working fluid (gas).

The reciprocating member 1 has an arm portion 1b connected to two output shafts 19 via a spherical bush 3, and a stator portion 20a and a rotor portion 20b are formed on each of the output shafts 19. As shown in FIG. The rotor portions 20b of the two oscillators 20 constituted of s are fixed. By the above configuration, the second embodiment functions as an expander and generates power by power taken out from the output shaft 18.

As described above, according to the second embodiment, only the initial period of the period in which the volume of the operating chamber space is increased, the high-pressure working fluid space is communicated with the operating chamber, Communication between the working fluid space and the working chamber can be realized without using the movable parts for the valve mechanism. Therefore, there is an effect that it is possible to provide a reciprocating volume expander having a small number of parts and high productivity reliability. Moreover, for the reason described in Japanese Patent Laid-Open No. 9-72275, it is also possible to reduce the excitation force due to the fluctuation of the drive torque and the inertia force of the reciprocating mass while being a reciprocating volume expander.

In addition, in the second embodiment, the discharge pipe 11 and the discharge port 16c function as suction pipes and suction ports for sucking low-pressure working fluid (gas), respectively, and the suction port 16b and the suction pipe ( 18 functions as a discharge port and a discharge pipe for discharging a high-pressure working fluid (gas), respectively, and with the output shaft 19 as a drive shaft, the drive shaft is replaced by two driving motors instead of the oscillator 20. By rotationally driving in the same manner, a gas compressor having the same features and effects as in the second embodiment can be obtained.

Next, a third embodiment of the present invention will be described with reference to Figs. 11 and 12 show an expansion and compressor as a third embodiment of the present invention. The third embodiment uses the refrigerant as the working fluid, but in the whole side sectional view of Fig. 11, the lower working chamber 7 functions as an inflator having the configuration as shown in Fig. 6, and the apparatus shown in Figs. Likewise, the operating chamber 7 alternately conducts with the suction port 22c and the discharge port 22d of the cylinder block 22 via the communication passage 21f of the reciprocating member 21.

On the other hand, an operating chamber 24 surrounded by the piston head 21a of the reciprocating member 21, the inner circumferential cylindrical surface 22a of the cylinder block 22, and the cylinder head 23 is formed. A suction port 21b is formed in this piston head portion 21a, and a suction valve plate 25 is mounted by a rivet 26. The rivet 26 constrains the suction valve plate 25 to rise from the upper end surface of the piston head portion 21a, and allows the inflow of refrigerant gas from the suction port 21b to the operation chamber 24 in the suction stroke. I'm letting you. A suction pipe 27 is connected to the cylinder block 22, and the expansion and the inside of the compressor of the third embodiment become suction pressure up to the rear surface of the piston head portion 21a, and the suction port 21b is The suction pipe 27 is in contact. The discharge head 23a is formed in the cylinder head 23, and the discharge valve plate 28 and the discharge valve press part 29 are fixed by the bolt (not shown). The cylinder head 23 is fixed to the cylinder block 22 by bolts with the discharge chamber cover 31 surrounding the discharge space 30. The discharge pipe 32 is connected to the discharge chamber cover 31. As a result, when the reciprocating member 21 reciprocates, the operation chamber 24 functions as a compressor.

The volumetric machine of Fig. 11 has both a volumetric expander portion which is an engine generating shaft power and a volumetric compressor portion which is a machine consuming power supplied from a drive shaft, but in the third embodiment the piston of the compressor portion is shown. The diameter of the head portion 21a is larger than the diameter of the piston head portion 21b of the expander portion and functions as a machine that consumes power as a whole. Therefore, the drive shaft 33 is rotationally driven by the motor 34 consisting of the stator part 34a and the rotor part 34b, but the theoretical required power is lower than the case of driving only the volumetric compressor part of the upper part. The type inflator is made smaller by the amount of power generated.

Fig. 12 shows a cycle configuration diagram when the expansion and compressor according to the third embodiment is assembled with a refrigeration cycle with a refrigeration and air conditioner. The central expansion and compressor 35 is an expansion and compressor, which is the third embodiment of FIG. In the figure, a thick line is a cycle pipe 36, and the arrow on a thick line shows the direction of refrigerant flow inside. Under normal refrigerant and operating conditions, the refrigerant gas, which has been expanded and pressurized in the compressor portion of the compressor 35 to high temperature and high pressure, is discharged from the discharge pipe 32, passes through the cycle pipe 36, and reaches the condenser 37, where It radiates and condenses to form a high pressure liquid refrigerant. A portion of the high pressure liquid refrigerant is then introduced from the inlet pipe 18 through the cycle pipe 36 into the expander and the expander portion of the compressor 35, where it is depressurized and partly gasified to increase the total volume to reduce the low pressure. It flows out from the discharge piping 11 in a gas-liquid two-phase state. The evaporator 38 is then passed through the cycle piping 36. The other part of the high pressure liquid refrigerant from the condenser 37 is configured to pass through a cycle pipe path provided in parallel with the path through the above expander, but is decompressed by other expansion means 39 provided in the path. As a result, a part of the gas is gasified and reaches the evaporator 38 after passing through the cycle piping 36 in a gas-phase two-phase state of low pressure. Further, the expansion means 39 is formed by throttling, such as an expansion valve or capillary tube in a conventional refrigeration cycle, and has a structure capable of recovering power by performing mechanical work to the outside in the expansion process such as an expander. It is not. In the evaporator 38, the liquid portion of the gas-phase two-phase refrigerant flowing through the two paths is endothermic and evaporates, and the whole becomes a low pressure gas and passes through the cycle pipe 36 and expands from the suction pipe 27 and the compressor ( It flows into the inside of 35). The refrigerant gas introduced into the expansion and the compressor 35 is pressurized by the compressor portion to become high temperature and high pressure, and then discharged from the discharge pipe 32 to form a closed loop of refrigerant circulation. 12, there is no expansion via one of two systems of refrigerant paths from the condenser 37 to the evaporator 38 and a path via the inflator portion of the compressor 35, and the entire amount of the refrigerant is expanded by throttling. Passing through means 39 is a refrigeration cycle configuration of the prior art.

In the prior art, energy is lost as a pressure loss when the entirety of the high pressure liquid refrigerant from the condenser passes through the same throttling means as the expansion means 39, and the lost energy becomes heat and is absorbed into the refrigerant so that the evaporator 38 The ability to endotherm, ie, the freezing ability, was reduced. On the other hand, in the refrigerating and air conditioning apparatus by the refrigeration cycle in which the expansion and the compressor are assembled according to the third embodiment, a part of the energy of the high-pressure liquid refrigerant, which has been heated as a pressure loss in the conventional throttle, is integrated with the compressor portion. In the expanded expander portion, power can be recovered as mechanical energy, and the power to be supplied to the compressor portion can be reduced. In particular, in the third embodiment, the pressure of the operating chamber 24 of the compressor portion and the pressure of the operating chamber 7 of the expander portion are integral with the piston head portion 21a and the piston head portion of the reciprocating member 21. Since it acts on the 21b, the force acting on the reciprocating member 21 due to their pressure partially cancels each other at the stage of the load, and the sliding portion between the arm portion 21b of the reciprocating member 21 and the spherical bush 3 is slid. The mechanical frictional loss can be reduced by reducing the moving load or the sliding load between the drive shaft 33 and the bearing portion 5a. In addition, as described above, the decrease in the freezing capacity in the freezing cycle is restored by the power recovered from the expander portion (the freezing capacity is increased with respect to the prior art). As a result, in the refrigerating and air-conditioning device by the refrigeration cycle in which the expansion and the compressor are assembled according to the third embodiment, since a larger refrigerating capacity can be obtained with a smaller power, there is an effect that the efficiency of the refrigerating air-conditioning device is improved. In addition, when the refrigerating and air-conditioning device incorporating the expansion and compressor as the third embodiment functions as a heating device as a heat pump, the heating capacity is usually the sum of the above-mentioned refrigeration capacity and the power consumption of the expansion and compressor 35. The increase in the refrigerating capacity and the decrease in power consumption cancel each other, but the efficiency as a heating device is improved by the amount of expansion and reduction in power consumption by the compressor 35.

In the cycle configuration diagram in FIG. 12, two refrigerant paths from the condenser 37 to the evaporator 38 are configured. If it is only a path through the expansion and the expander portion of the compressor 35, the suction volume (maximum volume) of the compressor operating chamber 24 and the suction volume of the expander operating chamber 7 in the expansion and compressor 35 When the ratio between the suction port 22b and the volume when the conduction is cut off is fixed at a constant value, the relationship between the suction pressure and the discharge pressure is restricted from the continuity of the mass flow rate in the loop of the refrigeration cycle. In the case where the volume ratio is inappropriate or the operating conditions such as the ambient temperature are greatly changed, there is a concern that the operating pressure conditions of the refrigerating cycle may be unnatural values. In the cycle configuration diagram of FIG. 12, the throttling amount of the expansion means 39 is adjusted in the refrigerant path of another system from the condenser 37 to the evaporator 38 so that the operating pressure conditions of the refrigeration cycle can be controlled. . However, when the suction volume ratio between each operation chamber mentioned above and operating conditions, such as an ambient temperature, are matched favorably, the suction volume in the expansion and at least one of each operation chamber of the compressor 35 is variable, and the capacity | capacitance is variable. In the case where control is possible, a path other than the path through the expansion and the inflator portion of the compressor 35 is not necessary, and power in the expansion process can be recovered from the total amount of the refrigerant circulating in the refrigeration cycle. Therefore, a more efficient refrigeration cycle can be configured. In addition, depending on the type of refrigerant and the operating pressure, a case may occur that does not involve a phase change from gas to liquid in the heat dissipation process in the condenser 37. However, if the condenser 37 functions as a radiator, good.

A fourth embodiment of the present invention will be described with reference to Figs. 13 to 16 show an expansion and compressor as a fourth embodiment of the present invention. This fourth embodiment is common to the third embodiment of FIG. 11 in that the lower operating chamber 41 functions as an inflator and the upper operating chamber 40 functions as a compressor in the entire side sectional view of FIG. Since the air is the working fluid, the expansion and the compressor do not need to be sealed in the container, and there is no difference between the external casing member such as the motor cover 14 in FIG.

One of the other differences is that a grease lubricated ball bearing 43 or needle bearing 44 is used in the bearing portion of the bearing frame 42. While the bearing portion in the third embodiment of Fig. 11 is used in an atmosphere of a refrigerant that elutes grease, it is used in an air atmosphere in the fourth embodiment, and lubrication by grease sealing is possible.

The following difference is that the diameter of the piston head portion 45c of the lower operating chamber 41 functioning as the expander has a size close to that of the piston head portion 45a of the upper operating chamber 40 functioning as the compressor. Is the point. Since the expansion and the compressor in the third embodiment of Fig. 11 are assembled and used in a refrigeration cycle, the refrigerant discharged from the expander portion continues to contain a large amount of liquid refrigerant, and the volume thereof is evaporated and gasified to the compressor. It is significantly smaller than the volume when inhaled. Therefore, the diameter of the piston head portion 21c of the expander portion is significantly smaller than the diameter of the piston head portion 21a of the compressor portion. On the other hand, in this embodiment which uses air as a working fluid, the use method (FIG. 17) which expands gas from the expander part to atmospheric pressure about the same amount of compressed air pressurized from atmospheric pressure in the compressor part is assumed. The diameter of the piston head portion 45c of the expander portion is set to approximately the same size as the diameter of the piston head portion 45a.

In this connection, the elliptical trajectory 46 of the opening to the outer circumferential cylindrical surface of the communication passage 45f of the reciprocating member 45 is shown in Figs. 14 and 15, but the radius of the open outer circumferential cylindrical surface is large. As a result, the length of the short axis becomes larger than that of the elliptic trajectory 15 in the first to third embodiments, which results in an expanded ellipse. In the inflator portion, the high pressure gas flows into the operating chamber 41 from the suction pipe 47 via the suction passage 48c provided on the cylinder block 48, the suction port 48d, and the communication passage 45f. Then, it expands in a sealed space and becomes a low pressure gas, and it flows out from the discharge piping 49 from the communication passage 45f via the discharge port 48e provided in the cylinder block 48, and the discharge passage 48f.

In addition, since the diameter of the piston head portion 45c of the expander portion is set to be approximately equal to the diameter of the piston head portion 45a of the compressor portion, the magnitude of the recovery power in the expander portion is increased. Since the power consumption is close to the magnitude of the power consumption, the power that must be supplied to the entirety of the expansion and the compressor is small, and the motor 51 for driving the drive shaft 50 has a small capacity.

The following difference is that in the fourth embodiment, the suction path of the compressor unit is different from the third embodiment, and the path from the suction pipe from the outside to the operation chamber 40 is expanded and the drive mechanism of the compressor is housed and moved. The point is configured without going through the internal space 52. The suction path of the compressor part is shown in FIG. 16 which is the K-K cross section in FIG. 16, the suction air which flowed into the suction path 48g of the cylinder block 48 from the left and right two suction pipes 53 is also the suction port 45g formed in the piston head part 45a of the reciprocating member 45. The inner space 45h of the piston head 45a is reached through the suction port 45b and sucked into the operating chamber 40 from the suction port 45b via the suction valve plate 25 mounted by the rivet 26. The suction passage 48g of the cylinder block 48 and the suction port 45g of the piston head portion 45a are electrically connected over the entire area of the suction stroke. Since the intake air does not pass through the expansion and the internal space 52 of the compressor, the lubricating oil sealed in the internal space 52 and the like can be prevented from mixing for lubrication of each sliding portion, thereby obtaining clean compressed air.

In the fourth embodiment, the coupling structure between the piston head portions 45a and 45c and the arm portion 45d of the reciprocating member 45 is different from that in the third embodiment. When the working pressure of the working fluid is relatively low as in the present embodiment, the diameter of the sliding portion between the arm portion 45d and the inner circumference of the spherical bush 3 is considerably small with respect to the diameter of the piston head portions 45a and 45c. Even if it is possible, the design which suppresses sliding surface pressure to a practical range is possible. In this case, a method of inserting the arm portion 45d through the piston head portions 45a and 45c as in this embodiment and integrally engaging the reciprocating member 45 by the nut 45e or the like is effective. When at least one of the diameters of the two piston heads is close to the diameter of the sliding part of the arm part of the reciprocating member as in the first to third embodiments, the center part of the arm part is thickened on the contrary, and the piston head penetrates the piston head. The method of inserting a part and fixing it integrally can be employ | adopted.

FIG. 17 shows a system configuration diagram when the expansion and compressor according to the fourth embodiment is applied to a fuel cell system. The expansion and compressor 56 in the right center is an expansion and compressor, which is the fourth embodiment of FIG. After passing through the air cleaner 58 on the upper right side, the air 57 in the air flows in from the suction pipe 53 of the expansion and the compressor 56, and after being compressed in the compressor unit, flows out of the discharge pipe 32 and is compressed. As air 59, it is supplied to the cathode portion 60a of the fuel cell stack 60. The supply of the compressed air 59 is because the fuel cell stack 60 can be made more efficient and downsized by supplying high density oxygen to the cathode portion 60a. On the other hand, the fuel gas 61 which is hydrogen or a gas containing hydrogen is supplied to the anode part 60b of the fuel cell stack 60. An ion permeable membrane 60c is disposed between the cathode portion 60a and the anode portion 60b, and hydrogen ions (+ ions) generated from hydrogen or a gas containing hydrogen supplied to the anode portion 60b are ions. In the process of permeating the permeable membrane 60c and generating moisture by combining with oxygen ions (− ions) generated from oxygen supplied to the cathode portion 60a, the cathode portion 60a and the cathode portion 60a are separated from the fuel cell stack 60. The power 60d can be taken out using the anode portion 60b as an electrode. The fuel gas 61 supplied to the anode portion 60b is discharged from the fuel cell stack 60 as the exhaust gas 62 after hydrogen is consumed and used for a heat source of a reformer (not shown) or the like. The compressed air 56 supplied to the cathode portion 60a consumes a portion of oxygen, but newly generated moisture is added and discharged from the fuel cell stack 60 as the high pressure exhaust air 63. Thereafter, the gas is reintroduced into the inflation and compressor 56 from the suction pipe 47, and after it is expanded in the expander portion, flows out of the discharge pipe 49 and finally discharged into the atmosphere as low pressure exhaust air 64.

Moreover, in the inflator part, it flows into the operation chamber 41 from the high pressure gas through the suction path 48c provided in the cylinder block 48, the suction port 48d, and the communication path 45f, and expands in a sealed space after that. It becomes low pressure gas, and flows out from the discharge pipe 49 from the communication passage 45f via the discharge port 48e provided in the cylinder block 48, and the discharge passage 48f.

In the fuel cell system incorporating the expansion and the compressor 56 of the fourth embodiment, since the power recovered by the power recovery mechanism is used for part of the power required to supply the compressed air 59, it must be newly supplied from the outside. The net power can be reduced. Further, in the conventional power recovery mechanism in which the compressor portion and the expander portion are independent, mechanical friction loss occurs in each of the compressor portion and the expander portion, and the total mechanical friction loss increases, whereas in the fourth embodiment, the third embodiment is implemented. As in the example, in the stage of the load acting on the reciprocating member 45 which is a common component, the sliding load of each sliding part is reduced and the mechanical friction loss is rather reduced. Thereby, the efficiency of expansion and the compressor 56 becomes high, and there exists an effect that the efficiency load of the whole fuel cell system using this increases further.

A fifth embodiment of the present invention will be described with reference to FIG. 18 shows a compressor as a fifth embodiment of the present invention. In the fifth embodiment, in the entire side sectional view of Fig. 18, the two operating chambers 65 formed at the upper and lower portions of the center both function as operating chambers of the compressor. That is, the fifth embodiment is a two cylinder compressor. The working fluid is carbon dioxide, and the pressure in the working chamber is very high, 4 to 5 times that of conventional pron-based refrigerants. On the other hand, the refrigerating capacity per unit volume of the refrigerant is also 4 to 5 times, and the stroke volume of the compressor which generates the same refrigerating capacity may be small. In the compressor shown in Fig. 18, the stroke volume is reduced by reducing only the diameters of the two piston head portions 66a in the reciprocating member 66, and the spherical bush 3 mounted on the driving arm portion 67a is reduced. The reduction in the stroke of the reciprocating motion of the reciprocating member 66 is not performed by reducing the amount of the center of gravity shifting from the rotational axis of the drive shaft 67. In addition, compared to a two-cylinder compressor having the same refrigeration capacity as a conventional prolon refrigerant, the diameter, the axial length, and the driving shaft 67 of the sliding portion between the arm portion 66b of the reciprocating member 66 and the spherical bush 3 are shown. ), The diameter of the sliding part and the axial length of the sliding part between the bearing frame 68 and the like are secured in the same size, and the hydraulic pressure area of the sliding part is the same as in the prior art. Such a design does not have a sliding part inside the reciprocating member 66 in which the pressure of the operating chamber directly acts in the mechanism of the volumetric machine employed in the present invention, so that the diameter of the piston part and the size of the sliding part, etc. All of these can be set independently of each other without restriction. Moreover, in the reciprocating mechanism by the conventional crank slider mechanism, since the piston pin in the small end of a cone rod is in the inside of the piston which the pressure of a working chamber acts directly, when the piston diameter is made small, the hydraulic pressure of the sliding part with a cone rod is reduced. It becomes difficult to keep the area equal to the prior art. In addition, in a rotary compressor such as a rolling piston system, when the width or diameter of the cylindrical rotor (piston) is reduced in order to reduce the area in which the pressure of the operating chamber directly acts, the eccentric pin portion and the rotation of the shaft inside the rotor are reduced. It is difficult to maintain the pressure-receiving area of the sliding portion with the electron inner circumferential surface as in the prior art.

Carbon dioxide, which is a working fluid, flows into the internal space 71 of the compressor from the suction pipe 70 attached to the cylinder block 69, and the piston head portion 66a from the suction port 66d provided in the reciprocating member 66. The inner space 66e of the cylinder is reached, and is sucked into the operating chamber 65 from the suction port 66f via the suction valve plate 73 attached to the piston head portion 66a by the rivet 72. After being compressed in the operation chamber 65, the discharge is discharged from the discharge port 74a formed in the cylinder head 74 to the discharge space 77 via the discharge valve plate 75 and the discharge valve presser 76. The discharge valve plate 75 and the discharge valve pressing portion 76 are fixed to the cylinder head 74 by bolts (not shown). The cylinder head 74 is fixed to the cylinder block 69 by bolts with the discharge chamber cover 78 surrounding the discharge space 77. The discharge pipe 79 is connected to the discharge chamber cover 78, and the high-pressure working fluid finally flows out of the compression chamber from the discharge chamber cover 78.

In the fifth embodiment, since the working fluid is carbon dioxide, the two piston head portions 66a of the reciprocating member 66 are both small in diameter, and the two inner circumferential cylindrical surfaces 69a of the cylinder block 69 into which they are inserted. The diameter is also small. If a portion thicker than the diameter of the inner circumferential cylindrical surface 69a is formed in the piston head portion 66a of the reciprocating member 66, it cannot be inserted into the inner circumferential cylindrical surface 69a of the cylinder block 69 during assembly. On the other hand, the diameter ratio of the arm portion 66b to the diameter of the inner circumferential cylindrical surface 69a is relatively larger than that of the conventional refrigerant, and when assembling the reciprocating member 66, the piston head portion 66a is shown in FIG. Strength cannot be secured in the structure in which the arm part 66b is inserted into the hole formed in the). Therefore, in the fifth embodiment, a thick portion is formed in the center of the arm portion 66b, and the piston head portion 66a is inserted into the hole provided therein to fix the pin 66c.

In the fifth embodiment, since the working fluid is carbon dioxide and the two-cylinder structure that performs the compression work in the two working chambers 65, the driving force is high because the stroke volume of each working chamber 65 is relatively small. The motor 80 is large, and the motor cover 81 which surrounds this and forms a sealed space is also large.

According to the fifth embodiment, firstly, even when a high-pressure working gas such as carbon dioxide is used, constraints when reducing the diameter of the piston head portion 66a of the reciprocating member 66, which is the member under pressure, Therefore, the design which does not increase the load of a sliding part is easy, and the design which does not increase a mechanical friction loss is possible. In addition, since it is not necessary to reduce the area of sliding parts, such as a bearing part at that time, the design which does not increase the sliding surface pressure of a sliding part is easy, and the design which does not reduce reliability is possible. Moreover, in the reciprocating member 66 which is a main component, even if the piston head part 66a is reduced, the strength of the engaging part with the arm part 66b can fully be ensured. That is, the practical use of a refrigeration air conditioning system using a working gas, which is a very high pressure such as carbon dioxide, but the operating gas originally present in nature and having a small load on the environment becomes easy.

According to the present invention, the reciprocating displacement type machine can make moving parts for the valve mechanism unnecessary, thereby improving the productivity and reliability.

In addition, according to the present invention, since the hydraulic pressure area of the operating chamber can be reduced without reducing the size and the hydraulic pressure area of the sliding parts such as the bearing by the volumetric compressor, the load of the sliding parts even if the ultra-high pressure refrigerant such as carbon dioxide is used as the working fluid. However, it is possible to not increase the sliding surface pressure, and there is an effect that a significant decrease in reliability and mechanical efficiency can be prevented.

Further, according to the present invention, the load acting on each sliding part of the volumetric machine integrating the compressor and the expander can be reduced, thereby improving the mechanical efficiency, enabling efficient power recovery by the expander, and assembling a power recovery mechanism. There is an effect that the efficiency of the entire system, such as a refrigeration cycle is greatly improved.

Claims (11)

A reciprocating member having a piston portion that changes the volume of the closed working space by the reciprocating motion and two arm portions extending opposite to each other in a direction perpendicular to the reciprocating direction of the piston portion, and a reciprocating portion of the working space which is part of the working space The piston portion is axially reciprocated by a guiding member for guiding the movement and two shaft members each having the same axial direction and rotating in the opposite directions, and supporting the arm portion at positions radially offset from the rotation axis. A volumetric machine reciprocating while oscillating around, at least part of a period in which the working fluid space of low pressure is in communication with the working chamber during a period in which the working space is increasing, and the volume of the working space is decreasing. Characterized in that the high-pressure working fluid space and the operating chamber in communication with the period It is positive displacement machines. A reciprocating member having a piston portion that changes the volume of the closed working space by the reciprocating motion and two arm portions extending opposite to each other in a direction perpendicular to the reciprocating direction of the piston portion, and a reciprocating portion of the working space which is part of the working space The piston portion is axially reciprocated by a guiding member for guiding the movement and two shaft members each having the same axial direction and rotating in the opposite directions, and supporting the arm portion at positions radially offset from the rotation axis. In a volumetric machine reciprocating while oscillating around, the high pressure working fluid space is in communication with the working chamber at least for a period of time during which the volume of the working space is increasing, and the volume of the working space is decreasing. Characterized in that the low pressure working fluid space and the operating chamber in communication Volumetric machine. A reciprocating member comprising two piston parts guided to another member to perform reciprocating motion and oscillating motion around an axis in the reciprocating direction, and two arm parts projecting to opposite sides in a direction perpendicular to the reciprocating direction, and the reciprocating part The guide member, which is another member for guiding the piston part of the moving member, and the relative rotation of one of the arm parts of the reciprocating member, respectively, at a position radially offset from the rotation axis while rotating in the opposite direction around the rotation axis of the same axis, respectively. It has two shaft members which can be supported in a change of direction, and a bearing member which supports rotation of the two shaft members as a component, and forms a closed space adjacent to each of the two piston parts of the said reciprocating member, Two working spaces, one operating space being the stand of the two shaft members It functions as a volumetric machine that transfers or compresses working fluid by changing its volume by rotation in the reverse direction, and the other working space drives the two shaft members to rotate in opposite directions by changing the volume by the pressure of the working fluid. A volumetric machine, characterized by functioning as a volumetric engine. 4. The two shaft members are each driven rotationally by an electric motor, the volumetric machine portion is a compressor using gas as the working fluid, and the volumetric engine portion operates at least a portion of the compressed gas in the compressor. A volumetric machine, characterized in that it is a fluid expander. Compression means for compressing the low-pressure refrigerant gas, cooling means for radiating heat from the compressed high-pressure high-pressure refrigerant gas, expansion means for depressurizing the cooled high-pressure refrigerant, and for evaporating the liquid refrigerant portion after decompression. In a refrigeration cycle having as a component a heating means and a pipe connecting them to form a closed cycle, the volumetric machine part of the volumetric machine of claim 4 is used as the compression means, and the volume of claim 4 as the expansion means. A refrigeration cycle and refrigeration and air conditioning equipment using a volumetric engine portion of a die-type machine. Compression means for compressing the low-pressure refrigerant gas, cooling means for radiating heat from the compressed high-pressure high-pressure refrigerant gas, expansion means for depressurizing the cooled high-pressure refrigerant, and for evaporating the liquid refrigerant portion after decompression. In a refrigeration cycle having as a component a heating means and a pipe connecting them to form a closed cycle, the volumetric machine part of the volumetric machine of claim 4 is used as the compression means, and the volume of claim 4 as the expansion means. A refrigeration cycle and a refrigeration / air conditioning device, characterized by a combination of a volumetric engine portion of a die machine and expansion means such as another throttle. A fuel cell system for supplying compressed air to a fuel cell stack, wherein the compressed air is produced in the volumetric machine portion of the volumetric machine of claim 4 and at least of the compressed air after consuming oxygen through the fuel cell stack. A fuel cell system, characterized by inducing a portion of the volumetric engine portion of the volumetric machine of claim 4 to expand and then open to the atmosphere. A reciprocating member comprising a piston part guided to another member to perform a reciprocating motion and a rocking motion around an axis in the reciprocating direction, and two arm parts protruding from each other in a direction perpendicular to the reciprocating direction, and the reciprocating member A guide member, which is another member for guiding the piston portion of the piston, and one of the arm portions of the reciprocating member relative to one another in a position radially offset from the rotation axis while rotating in the opposite direction about the rotation axis of the same axis, It has two shaft members which can be supported to be changed, and a bearing member which supports rotation of the two shaft members as a component, and forms a closed space adjacent to the said reciprocating member, and makes it the working space, When reciprocating the reciprocating member by the reverse rotation of the shaft member In the volume change and positive displacement machines for performing the transfer and compression of the working fluid in the working space, positive displacement compressor characterized in that the compress it using the carbon dioxide as the working fluid. A refrigeration air conditioner comprising carbon dioxide as a refrigerant using the volumetric compressor of claim 8. A reciprocating member comprising a piston part guided to another member to perform a reciprocating motion and a rocking motion around an axis in the reciprocating direction, and two arm parts projecting to opposite sides in a direction perpendicular to the reciprocating direction, and the reciprocating member A guide member, which is another member for guiding the piston portion of the piston, and one of the arm portions of the reciprocating member relative to one another in a position radially offset from the rotation axis while rotating in the opposite direction about the rotation axis of the same axis, It has two shaft members which can be supported to be changed, and a bearing member which supports rotation of the two shaft members as a component, and forms a closed space adjacent to the said reciprocating member, and makes it the working space, When reciprocating the reciprocating member by the reverse rotation of the shaft member In a volumetric machine for varying the volume of the working space and for conveying or compressing a working fluid, the reciprocating member is formed by inserting a member having a piston portion in the center of a member having two arm portions. compressor. A reciprocating member having a piston portion that changes the volume of the closed working space by the reciprocating motion and two arm portions extending opposite to each other in a direction perpendicular to the reciprocating direction of the piston portion, and a reciprocating portion of the working space which is part of the working space The axial direction of the reciprocating motion direction is provided by a guide member for guiding the movement and two shaft members each having the same axial direction and rotating in opposite directions to each other and supporting the arm portions at positions radially offset from the rotation axis. In a volumetric machine reciprocating while oscillating around, the guide member has a communication portion communicating with a working fluid space in which a working fluid moves, the communicating portion being connected to a communication path leading to the working space provided in the piston part. A volumetric machine, characterized in that communicating.