WO2016006685A1

WO2016006685A1 - Displacement machine

Info

Publication number: WO2016006685A1
Application number: PCT/JP2015/069907
Authority: WO
Inventors: 直毅鹿園; 早瀬　功
Original assignee: 国立大学法人東京大学
Priority date: 2014-07-11
Filing date: 2015-07-10
Publication date: 2016-01-14
Also published as: EP3168473B1; JP2016017513A; EP3168473A4; EP3168473A1; JP6449576B2

Abstract

Second arm sections (54a, 54b) formed as inner peripheral cylindrical surfaces that have, as the central axis, an axis line that is parallel to the axis of rotation of shaft member (50a, 50b), support first arm sections (44a, 44b) such that the spherical centers (P1a, P1b) of outer peripheral spherical sections (45a, 45b) that are attached to the first arm sections (44a, 44b) are bound to the central axis line of the second arm sections (54a, 54b).

Description

Positive displacement machine

The present invention relates to a positive displacement machine, and more particularly to a low vibration positive displacement machine in which a piston reciprocates and swings.

Conventionally, this type of positive displacement machine includes two pistons guided by a guide cylindrical member and a pair of second pistons arranged symmetrically from the center of the two pistons in a direction perpendicular to the central axis of the guide cylindrical member. A reciprocating member having one arm portion, a pair of shaft members disposed symmetrically so as to be orthogonal to the central axis of the guide cylindrical member, and the shaft member at a position displaced from the rotation axis of each shaft member. A pair of second arm portions that are attached to hold each first arm portion and a pair of working chambers that change in volume by the reciprocating motion of the two pistons, and the reciprocating member reciprocates with a swinging motion. A thing which moves is proposed (for example, refer to patent documents 1). FIG. 19 is a configuration diagram showing an outline of the configuration of a conventional positive displacement machine 920. FIG. 20 shows a part of the reciprocating member 940 and the

shaft portions

950a and 950b that are swinging upward in FIG. FIG. 21 is an explanatory view of a part of the reciprocating member 940 and the

shaft portions

950a and 950b that are swinging as viewed from the right side in FIG. In addition, the positive displacement type machine 920 has a support structure for the

first arm portions

944a and 944b by the

second arm portions

954a and 954b for comparison with the positive displacement type machine 20 as an embodiment of the present invention described later. Except for this, the configuration was the same as that of the positive displacement machine 20 of the example.

As shown in FIG. 19, the conventional positive displacement machine 920 includes a cylindrical guide cylinder member 930 having a central axis in the vertical direction (Y-axis direction) in the figure, and a pair of

pistons

942a, 942b is guided to reciprocate in the vertical direction (Y-axis direction) in the figure, and to reciprocate around the central axis of the guide cylindrical member 930 (around the Y-axis), and at the center of the guide cylindrical member 930 A pair of

shaft members

950a and 950b having rotational axes arranged on a straight line (on the Z axis) orthogonal to the central axis, a pair of working

chambers

962a and 962b whose volume is changed by the reciprocating motion of the

pistons

942a and 942b, and operation A pair of high-

pressure chambers

966a and 966b connected to the

chambers

962a and 962b via discharge valves 967a and 967b, and

shaft members

950a and 950b, respectively. Tagged pair of electric motors 970a, comprises a 970b, a. A pair of

first arm members

944 a and 944 b are attached to the center of the reciprocating member 940 so as to be orthogonal to the central axis of the guide cylindrical member 930 and to be symmetric with respect to the central axis. Yes. A pair of

second arm portions

954a and 954b that support the

first arm portions

944a and 944b at positions displaced from the rotation shafts are provided at one end portions (end portions on the reciprocating member 940 side) of the

shaft members

950a and 950b. A pair of

main weight balances

958a and 958b are attached so that the direction of centrifugal force is the opposite direction. In addition, a pair of

shaft members

950a and 950b is connected to the other end (the end opposite to the reciprocating member 940) so that the centrifugal force is in the direction opposite to the

main weight balance

958a and 958b.

Sub-weight balances

959a and 959b are attached.

As shown in FIG. 20, outer peripheral

spherical surface portions

945a and 945b are attached to the

first arm members

944a and 944b so as to be movable in the arm axis direction. The

second arm portions

954a and 954b are formed in a substantially cylindrical shape with an inner peripheral spherical surface, and the outer peripheral

spherical surface portions

945a and 945b of the

first arms

944a and 944b are held by spherical pairs even with the inner peripheral spherical surface. With such a support structure, when the

shaft members

950a and 950b are rotationally driven so as to be relatively reversely rotated, the

second arm portions

954a and 954b are also relatively reversely rotated. Accordingly, the

first arm portions

944a and 944a are The outer peripheral

spherical surface portions

945a and 945b of the 944b perform an accurate circular motion with the relative movement of the arm portion in the axial direction, and cause the reciprocating member 940 to perform a swinging motion and a reciprocating motion.

The fluid passages 963a and 963b for supplying the working fluid to the

working chambers

962a and 962b are formed in the

pistons

942a and 942b, and the working fluid space 960 between the

pistons

942a and 942b is formed in the fluid passages 963a and 963b.

Suction valves

964a and 964b are attached which open when the pressure in the

working chambers

962a and 962b becomes lower than the pressure in the chamber. Discharge valves that open when the pressure in the

working chambers

962a and 962b is higher than the pressure in the high-

pressure chambers

966a and 966b are provided in the

partition walls

965a and 965b between the

working chambers

962a and 962b and the high-

pressure chambers

966a and 966b. 967a and 967b are attached, and

outflow pipes

968a and 968b are attached to the high-

pressure chambers

966a and 966b. Furthermore, an inflow pipe (not shown) that communicates with the working fluid space 960 is attached to the case 922. Therefore, the working fluid flows into the working fluid space 960 from the inflow pipe, and is supplied to the

working chambers

962a and 962b via the fluid flow paths 963a and 963b and the

suction valves

964a and 964b by the reciprocating motion of the

pistons

942a and 942b. It flows into the

high pressure chambers

966a and 966b through the valves 967a and 967b, and flows out from the

outflow pipes

968a and 968b.

In the conventional positive displacement machine 920, the inertial force Fpy in the central axis direction (Y-axis direction) is generated as the reciprocating member 940 reciprocates. This inertial force Fpy is caused by the Y-axis direction component Fsy of the total centrifugal force Fs by the

second arm portions

954a and 954b attached to the shaft members 950a and 95b, the

main balance weights

958a and 958b, and the

auxiliary weight balances

959a and 959b. It can be completely erased. When the

shaft members

950a and 950b are reversed, the components Fsx in the direction perpendicular to the reciprocating direction of the centrifugal force (X-axis direction) are reversed in sign, so that they are canceled out between the

shaft members

950a and 950b reversed. Will be completely erased. Moreover, in the positive displacement type machine 920, as described above, the movement of each component member and the force acting between the component members are symmetrical with respect to the central axis of the reciprocating member 940. The inertia force in the rotation axis direction (Z-axis direction) of the

shaft members

950a and 950b due to the movement of the movable member, the torque around the Z axis due to the inertia force, and the torque around the X axis due to the inertia force are not generated. Therefore, in the positive displacement type machine 920, the inertial force in the three axes (X axis, Y axis, Z axis) direction of the rectangular coordinate system and the torque around the three axes due to the inertial force, Generation of excitation force other than torque can be made zero. On the other hand, most of the torque around the Y axis can be eliminated by adjusting the size of the

main balance weights

958a and 958b and the size of the

auxiliary weight balances

959a and 959b. As a result, the positive displacement type machine 920 has very little vibration to the surroundings.

Japanese Patent Laid-Open No. 9-92275 (FIGS. 7 to 11)

In the conventional positive displacement type machine 920, by shortening the arm length of the

first arm portions

944a and 944b, the bending moment of the base portion of the

first arm portions

944a and 944b can be reduced, or the

main weight balances

958a and 958b can be reduced. Although the couple of centrifugal force due to the X-axis direction component can be reduced to reduce the size of the

auxiliary weight balances

959a and 959b, on the other hand, the maximum swing angle (oscillation piece amplitude angle) of the reciprocating member 940 can be achieved. ) Becomes larger. In the positive displacement type machine 920, the diameter of the

pistons

942a and 942b (the bore diameter of the cylinder) is reduced to reduce the bearing load and reduce the mechanical friction loss, or the gap volume (the working chamber 962a, The volume efficiency can be increased by reducing the volume of the working fluid that remains and re-expands by reducing the volume at the top dead center of 962b, but on the other hand, in the reciprocating motion of the reciprocating member 940, Since the stroke becomes longer, the maximum swing angle (swing piece amplitude angle) of the reciprocating member 940 is increased. As the maximum swing angle (swing piece amplitude angle) increases, the torque around the Y axis, which is difficult to completely erase, increases and the surroundings are vibrated.

The main purpose of the positive displacement machine of the present invention is to propose a lower displacement vibration displacement machine.

容積 The positive displacement machine of the present invention employs the following means in order to achieve the main object described above.

The positive displacement machine of the present invention is
A cylindrical guide cylindrical member;
A piston portion that is guided by the inner peripheral surface of the guide cylindrical member and reciprocates in the direction of the central axis of the guide cylindrical member and swings around the central axis, and is orthogonal to the central axis of the guide cylindrical member and the central axis A reciprocating member having a pair of first arm parts attached to the piston part so as to be symmetrical with respect to
A pair of shaft members disposed so as to be orthogonal to the central axis of the guide cylindrical member and symmetrical with respect to the central axis;
A pair of second arm portions attached to the pair of shaft members so as to support the pair of first arm portions at positions displaced from the rotation axes of the pair of shaft members,
A working chamber in which a volume change occurs as the piston part reciprocates;
A positive displacement machine comprising:
The second arm portion supports the specific point predetermined in the first arm portion so as to be movably restrained on an axis parallel to the rotation axis of the shaft member.
It is characterized by that.

In the positive displacement machine according to the present invention, the first arm portion is connected to the second arm so that a predetermined specific point in the first arm portion is movably restrained on an axis parallel to the rotation axis of the shaft member. By supporting at the portion, the vibration can be further reduced. Here, “restrained to be movable on the axis” means that only movement on the axis is possible. The positive displacement machine of the present invention includes a machine (such as an engine) that causes a reciprocating motion and a rocking motion to be generated in a reciprocating member by supplying a pressure fluid to a working chamber to generate a rotational driving force on a pair of shaft members. Or a machine (such as a compressor) that causes a reciprocating motion and a swinging motion of the reciprocating member by supplying a rotational driving force to the pair of shaft members, thereby causing a change in the volume of the working chamber. You can also. In these cases, the piston part has two pistons symmetrically across the pair of first arm parts, and two working chambers are formed so as to correspond to each of the two pistons. You can also.

In such a positive displacement machine of the present invention, the first arm portion has an outer peripheral spherical surface portion having a spherical center as the specific point, and the second arm portion is an axis parallel to the rotation axis of the shaft member. It is also possible to have an inner peripheral cylindrical portion that is arranged on a line and that slidably holds the outer peripheral spherical portion.

In the positive displacement machine of the present invention, the first arm portion has an outer peripheral spherical surface portion having a spherical center as the specific point, and the second arm portion holds the outer peripheral spherical surface portion and the shaft member. It is also possible to have an inner circumferential spherical surface portion that moves on an axis parallel to the rotation axis. In this way, since the outer peripheral spherical surface portion is held by the inner peripheral spherical surface portion, the force exchange between the first arm portion and the second arm portion can be performed by surface contact. In the positive displacement machine according to this aspect of the present invention, the inner peripheral spherical portion is formed in a cylindrical shape on the outer periphery, and the second arm portion is configured such that the inner peripheral spherical portion is positioned with respect to the rotation axis of the shaft member. It is also possible to have an inner circumferential cylindrical portion that is held so as to be movable on parallel axes. In this way, the movement of the outer peripheral spherical surface portion along the axis parallel to the rotation axis of the shaft member accompanying the reciprocating motion and the swinging motion of the reciprocating member can be smoothly performed, and the mechanical friction loss is reduced. be able to.

In the positive displacement machine of the present invention in which the inner peripheral spherical portion is held by the inner peripheral cylindrical portion of the second arm portion, the inner peripheral spherical portion is configured such that the inner peripheral side around the rotation axis of the shaft member is greater than the outer peripheral side. It is formed so that it may leave | separate from 1 arm part, and the said inner peripheral cylindrical part shall hold | maintain the said inner peripheral spherical surface part non-rotatably around the axis | shaft parallel to the rotating shaft of the said shaft member. it can. In this way, when the reciprocating member reaches the maximum swing angle (swing piece amplitude angle), the first arm portion and the inner peripheral side of the inner peripheral spherical surface of the second arm portion around the rotation axis of the shaft are The contact and interference can be suppressed, and the maximum swing angle (swing piece amplitude) of the reciprocating member can be further increased. In this case, you may form so that the end surface of an inner peripheral spherical surface part may become a slope with respect to the rotating shaft of a shaft member.

In the positive displacement machine of the present invention in which the first arm portion has an outer peripheral spherical portion, the outer peripheral spherical portion is supported so as to be rotatable about the central axis of the first arm portion and immovable in the central axis direction. It can also be. In this way, the rotation of the outer peripheral spherical surface portion around the central axis of the reciprocating member and the swinging motion of the reciprocating member can be performed smoothly, and the mechanical friction loss can be reduced.

Further, in the positive displacement machine of the present invention, the first arm portion has an inner peripheral spherical surface portion having a spherical center as the specific point, and the second arm portion is held by the inner peripheral spherical surface portion, An outer peripheral spherical surface portion that can move on an axis parallel to the rotation axis of the shaft member may be provided. In this case, the inner circumferential spherical surface portion may be supported so as to be rotatable around the central axis of the first arm portion and immovable in the central axis direction. In this case, the rotation of the inner peripheral spherical surface portion around the center axis of the first spherical surface portion accompanying the reciprocating motion and the swinging motion of the reciprocating member can be smoothly performed, and the mechanical friction loss can be reduced. .

Further, in the positive displacement machine according to the present invention, the second arm portion is formed as an inner peripheral cylindrical surface, and the first arm portion has two planes perpendicular to the reciprocating direction of the reciprocating member. A substantially barrel-shaped hinge portion and slidably contact with the two planes of the hinge portion, and slidably contact with the inner peripheral cylindrical surface of the second arm portion, and disposed on the central axis of the hinge portion. And a sliding portion integrated with the hinge portion by a pin.

It is a block diagram which shows the outline of a structure of the positive displacement machine 20 as one Example of this invention. It is explanatory drawing which shows the state of the reciprocating member 40 which reciprocates with a rocking | fluctuating motion. It is explanatory drawing which looked at the reciprocating member 40 which reciprocates with rocking | fluctuation movement from the upper direction in FIG. It is explanatory drawing which expands and demonstrates the 1st arm part 44a and the 2nd arm part 54a of the reciprocating member 40 which reciprocates with rocking | fluctuation motion. It is explanatory drawing which looked at a part of reciprocating member 40 and

shaft parts

50a and 50b which reciprocate with a rocking | fluctuating movement from the upper direction in FIG. It is explanatory drawing which looked at a part of reciprocating member 40 and

shaft parts

50a, 50b which are rocking | fluctuated from the right side in FIG. It is explanatory drawing which shows the relationship between the rotation angle (theta) of the

shaft members

50a and 50b, the dimensionless swing torque, and the excitation torque when the swing piece amplitude angle of the positive displacement machine 20 is 15 degrees. It is explanatory drawing which shows the relationship between the rotation angle (theta) of the

shaft members

50a and 50b, the dimensionless swing torque, and excitation torque when the swing piece amplitude angle of the positive displacement machine 20 of an Example is 25 degree | times. It is explanatory drawing which shows the relationship between rotation angle (theta) of

shaft members

950a and 950b, and non-dimensionalized swing torque and excitation torque when the swing piece amplitude angle of the positive displacement type machine 920 is 15 degrees. It is explanatory drawing which shows the relationship between rotation angle (theta) of

shaft members

950a and 950b, and non-dimensionalized swing torque and excitation torque when the swing piece amplitude angle of the positive displacement type machine 920 is 25 degrees. It is explanatory drawing which expands and shows the support structure of the 1st arm part 144a by the 2nd arm part 54a in the positive displacement type machine of a 1st modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 44a by the 2nd arm part 154a in the positive displacement type machine of a 2nd modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 144a by the 2nd arm part 154a in the positive displacement machine of a 3rd modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 144a by the 2nd arm part 254a in the positive displacement type machine of a 4th modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 344a by the 2nd arm part 354a in the positive displacement machine of a 5th modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 444a by the 2nd arm part 354a in the positive displacement machine of a 6th modification. It is explanatory drawing which expands and shows the support structure of the 1st arm part 544a by the 2nd arm part 554a in the positive displacement type machine of a 7th modification. FIG. 8 is a cross-sectional view showing the AA cross section of FIG. 7. It is a block diagram which shows the outline of a structure of the positive displacement machine 920 of a prior art example. It is explanatory drawing which shows the mode of the support of

1st arm member

944a, 944b by

2nd arm part

954a, 954b. It is explanatory drawing which looked at a part of reciprocating member 940 and

shaft part

950a, 950b which are rocking | fluctuated from the right side in FIG.

Next, modes for carrying out the present invention will be described using examples.

FIG. 1 is a configuration diagram showing an outline of the configuration of a positive displacement machine 20 as an embodiment of the present invention. The positive displacement machine 20 of the embodiment is configured as a compressor that pressurizes a gas that is a working fluid, and as illustrated, a cylindrical guide cylindrical member having a central axis in the vertical direction (Y-axis direction) in the drawing. 30 and a pair of

pistons

42a, 42b are guided by the guide cylindrical member 30 and reciprocate in the vertical direction (Y-axis direction) in the figure, and swing around the central axis of the guide cylindrical member 30 (around the Y-axis). Reciprocating motion of the reciprocating member 40, a pair of

shaft members

50a, 50b arranged at the center of the guide cylindrical member 30 and having a straight line (Z-axis) orthogonal to the central axis as a rotation axis, and

pistons

42a, 42b. A pair of working chambers 62a and 62b whose volume changes due to the above, a pair of

high pressure chambers

66a and 66b adjacent to the working chambers 62a and 62b via

partition walls

65a and 65b, and a pair of

shaft members

50a and 50b. A pair of electric motor 70a which Re is attached respectively, comprises a 70b, a case 22 for housing them, a.

The reciprocating member 40 has a pair of

first arm members

44a and 44b at the center thereof so as to be orthogonal to the central axis (Y axis) of the guide cylindrical member 30 and to be symmetric with respect to the central axis. Is attached. Outer

spherical surfaces

45a and 45b having spherical centers P1a and P1b on the arm axis are formed or attached to the ends of the

first arm members

44a and 44b.

The

fluid passages

63a and 63b for supplying the working fluid to the working chambers 62a and 62b are formed in the

pistons

42a and 42b. The working fluid space 60 between the

pistons

42a and 42b is formed in the

fluid passages

63a and 63b.

Suction valves

64a and 64b are attached which open when the pressure in the working chambers 62a and 62b becomes lower than the pressure in the first chamber. Further, the

partition walls

65a and 65b between the working chambers 62a and 62b and the

high pressure chambers

66a and 66b are discharged when the pressure in the working chambers 62a and 62b becomes higher than the pressure in the

high pressure chambers

66a and 66b. Valves 67a and 67b are attached, and

outflow pipes

68a and 68b are attached to the high-

pressure chambers

66a and 66b. Further, an inflow pipe (not shown) communicating with the working fluid space 60 is attached to the case 22. Therefore, the working fluid flows into the working fluid space 60 from the inflow pipe, and is supplied to the working chambers 62a and 62b via the

fluid flow paths

63a and 63b and the

suction valves

64a and 64b by the reciprocating motion of the

pistons

42a and 42b. It flows into the

high pressure chambers

66a and 66b through the valves 67a and 67b, and flows out from the

outflow pipes

68a and 68b.

The

shaft members

50a, 50b are rotatably supported by

ball bearings

51a, 51b, 52a, 52b, and are reciprocated at positions deviated from the rotation axis of one end thereof (end on the reciprocating member 40 side). A pair of

second arm portions

54a and 54b that support the

first arm portions

44a and 44b of the member 40 are attached. The

second arm portions

54a and 54b are formed as inner peripheral cylindrical members having an axis parallel to the rotation axis of the

shaft members

50a and 50b as a central axis, and the first arm members 4a and 4b are formed in the inner peripheral cylinder. The outer peripheral

spherical surface portions

45a and 45b of 44b are slidably accommodated. Here, when the

shaft members

50a and 50b are rotationally driven so as to be relatively reversely rotated, the

second arm portions

54a and 54b are also relatively reversely rotated, and accordingly, the

first arm portions

44a and 44b are rotated. The outer peripheral

spherical surface portions

45a and 45b revolve with some reciprocating motion of the

shaft members

50a and 50b in the axial direction, and the reciprocating member 40 performs reciprocating motion with rocking motion. 2 is an explanatory view showing a state of the reciprocating member 40 that reciprocates with a swinging motion. FIG. 3 shows the reciprocating member 40 that reciprocates with a swinging motion as viewed from above in FIG. FIG. FIGS. 2 and 3 (a) to 3 (e) show states each time the

shaft members

50a and 50b rotate 90 degrees from the state where the reciprocating member 40 is located at the center in the reciprocating motion. As shown in the figure, the reciprocating member 40 performs a reciprocating motion with an amplitude 2ε, which is a top dead center in FIG. 2B and a bottom dead center in FIG. 2D, and FIGS. 3A and 3E. Oscillates with a counterclockwise oscillating piece amplitude angle θmax and with a oscillating piece amplitude angle θmax clockwise in FIG. In FIG. 2, the front outer peripheral spherical surface portion 45a revolves counterclockwise, and the rear outer peripheral spherical surface portion 45b revolves clockwise. Accordingly, the shaft member 50a rotates counterclockwise. In addition, it can be seen that the shaft member 50b rotates clockwise.

FIG. 4 is an explanatory diagram for enlarging and explaining the first arm portion 44a and the second arm portion 54a of the reciprocating member 40 that reciprocates with a swinging motion. 4A shows the state of top dead center (rocking angle 0 degree) as seen from the same direction as FIG. 1, and FIG. 4B shows the maximum rocking angle (rocking piece amplitude angle θmax). The state at the time is seen from above in FIG. As shown in the drawing, the outer peripheral spherical surface portion 45a attached to the first arm portion 44a slides with respect to the inner peripheral cylindrical surface of the second arm portion 55a by the swinging motion and moves in the axial direction of the second arm portion 54a. Move by ΔL. At this time, the spherical center P1a of the outer peripheral spherical surface portion 45a is restrained on the axis of the second arm portion 54a. The ball centers P1a and P1b are also referred to as “specific points P1a and P1b” in this embodiment.

A pair of main weight balances 58a, 58b is attached to one end of the

shaft members

50a, 50b so that the direction of centrifugal force is opposite to the

second arm members

54a, 54b. At the other end of 50a, 50b (the end opposite to the reciprocating member 40), a pair of sub-weight balances 59a so that the direction of the centrifugal force is in the direction opposite to the main weight balances 58a, 58b. , 59b are attached.

In the positive displacement machine 20 of the embodiment configured in this way, the inertial force in the three-axis (X axis, Y axis, Z axis) directions of the rectangular coordinate system is the same as the conventional positive displacement machine 920 illustrated in FIG. Among the torques around the three axes due to the inertial force, the generation of an excitation force other than the torque around the Y axis can be made zero. Hereinafter, the torque around the Y axis of the positive displacement machine 20 of the embodiment will be described using a comparison with the positive displacement machine 920 of the conventional example.

FIG. 5 is an explanatory view of a part of the reciprocating member 40 and the

shaft portions

50a and 50b that are swinging as viewed from above in FIG. 1, and FIG. 6 is a reciprocating member 40 that is swinging. FIG. 5 is an explanatory view of a part of the

shaft portions

50a and 50b as viewed from the right side in FIG. The torque Np1 around the Y axis due to the inertial force in the swing motion around the Y axis of the reciprocating member 40 of the positive displacement machine 20 is expressed as Ip1 as the moment of inertia around the Y axis of the reciprocating member 40, and the angular acceleration due to the swing motion. When αp1, it is expressed by the following equation (1).

The distance from the central axis of the reciprocating member 40 to the spherical centers P1a and P1b (specific points P1a and P1b) of the outer peripheral

spherical surface portions

45a and 45b of the

first arm portions

44a and 44b is 11 (see FIG. 5), and the shaft member 50a. , 50b and the center axis La, Lb on the inner peripheral cylindrical surface of the

second arm portions

54a, 54b is r1 (see FIG. 6), and the rotation angle θ of the

shaft members

50a, 50b is used. The X coordinate x1 of the central axis La is expressed by the following equation (2). In addition, x1 of this formula (2) is also the X coordinate of the specific point P1a. The swing angle θp1 is expressed as equation (3) from FIG. The swing piece amplitude angle θmax1 in the swing motion of the reciprocating member 40 is expressed as Formula (4) from Formula (3), and is substituted into Formula (3) to obtain Formula (5).

The component Fsx in the X-axis direction of the total centrifugal force Fs of the

shaft members

50a and 50b is canceled out by the

shaft members

50a and 50b that rotate in reverse as the inertial force. And remains as torque around the Y axis. Main weight balances 58a and 58b are attached to the

shaft members

50a and 50b so that the direction of the centrifugal force is opposite to the

second arm portions

54a and 54b, and the direction of the centrifugal force is the first direction. The

sub-weight balances

59a and 59b are attached so as to be in the same direction as the two-

arm portions

54a and 54b, but the main weight balances 58a and 58b are dominant in the centrifugal force generated by each part. Therefore, the centrifugal force Fs is in the direction of the centrifugal force of the main weight balances 58a and 58b. When the rotational angular velocity of the

shaft members

50a and 50b is ω, the X-axis direction component Fsx of the centrifugal force Fs is expressed by the following equation (6), where mr is a constant. Since this acts on the positions of the Z-axis coordinates lmr, −lmr, the torque around the Y-axis is expressed by the equation (7). Here, the two constants lmr and mr can be adjusted to arbitrary values independently of each other by adjusting two variables of the sizes of the main weight balances 58a and 58b and the sub weight balances 59a and 59b. . When the

shaft members

50a and 50b are rotating at a constant speed, ω is also a constant. At this time, the torque Ns becomes a cosine function of the rotation angle θ of the

shaft members

50a and 50b, and has only a rotation primary component.

Since the angular acceleration αp1 due to the rocking motion is obtained by differentiating the rocking angle θp1 twice with respect to time t, it can be expressed as the following equation (8) using θ = ωt. Substituting this into equation (1) yields equation (9). For the case where the swing piece amplitude angle θmax1 is 15 degrees (0.263 rad) and 25 degrees (0.436 rad), Expression (5) is substituted into Expression (9) and normalized by dividing by Ip1 · ω2. When the oscillation torque Np1 * is further expanded by Fourier series, Expressions (10) and (11) are obtained. In addition, since the coefficient becomes small so that it can be disregarded after the fourth term on the right side of Expression (10) and Expression (11), the description is omitted.

Looking at the coefficients of the respective terms on the right side of the equations (10) and (11), the torque Np1 around the Y axis due to the inertial force generated by the swinging motion of the reciprocating member 40 is the shaft member 50a corresponding to the first term. , 50b, the primary rotation component is dominant, but they are eliminated by adjusting lmr and mr in equations (6) and (7) to cancel with the torque around the Y axis due to the centrifugal force of the shaft member. be able to. Therefore, the component that vibrates the surroundings is a higher-order term after the second term on the right side of Equation (10) and Equation (11).

In the conventional positive displacement machine 920 (see FIGS. 19, 20, and 21), the torque Np2 around the Y axis due to the inertial force in the swinging motion around the Y axis is the moment of inertia around the Y axis of the reciprocating member 940. Is represented by the following formula (12), where Ip2 is the angular acceleration due to the swing motion.

If the amount of deviation of the spherical center P2a of the outer peripheral spherical surface portion 945a supported by the second arm portion 954a from the spherical pair from the rotation axis of the shaft member 950a is r2 (see FIG. 21), the X-axis coordinate x2 of the spherical center P2a Is expressed by equation (13), and if the Z-axis coordinate of the ball center P2a is 12 (see FIG. 20), the swing angle θp2 is expressed by equation (14).

Since the angular acceleration αp2 due to the rocking motion is obtained by differentiating the rocking angle θp2 twice with respect to time t, it can be expressed as the following equation (15) using θ = ωt. Substituting this into equation (12) yields equation (16).

The swinging piece amplitude angle θmax2 in the swinging motion of the reciprocating member 940 is expressed as Formula (17) from Formula (14), and this is substituted into Formula (14) to obtain Formula (18). For the case where the swing piece amplitude angle θmax2 is 15 degrees (0.263 rad) and 25 degrees (0.436 rad), Expression (18) is substituted into Expression (16) and normalized by dividing by Ip · ω2. When the oscillation torque Np2 * is further expanded by Fourier series, Expressions (19) and (20) are obtained. In addition, since the coefficient becomes small so that it can be disregarded after the fourth term on the right side of Expression (19) and Expression (20), the description is omitted.

Also in the positive displacement type machine 920, when looking at the coefficients of the terms on the right side of the equations (19) and (20), the torque Np2 around the Y axis due to the inertial force generated by the swinging motion of the reciprocating member 940 is: The primary rotation components of the

shaft members

950a and 950b corresponding to the first term are dominant, but they are adjusted by adjusting lmr and mr in the equations (6) and (7) to obtain the Y axis by the centrifugal force of the shaft member. It can be erased by canceling with the surrounding torque. Therefore, the component that vibrates the surroundings is a higher-order term after the second term on the right side of Equation (19) and Equation (20).

In the positive displacement machine 20 of the embodiment, the expression (10) and the second term on the right side of the expression (11) are compared with the second expression on the right side of the expression (20) in the conventional displacement type machine 920. Then, since the coefficient of the positive displacement machine 20 of the embodiment is smaller regardless of the swing piece amplitude angle θmax, the positive displacement machine 20 of the embodiment is compared with the positive displacement volume machine 920 of the conventional example. Thus, the excitation torque for exciting the surroundings becomes small.

7 and 8 show the rotation angle θ of the

shaft members

50a and 50b and the dimensionless swing torque and excitation torque when the swing piece amplitude angle of the positive displacement machine 20 of the embodiment is 15 degrees and 25 degrees. 9 and 10 are diagrams showing the relationship between the rotation angle θ of the

shaft members

950a and 950b when the swing piece amplitude angle of the positive displacement type machine 920 is 15 degrees and 25 degrees, and It is explanatory drawing which shows the relationship between the dimensioned swing torque and excitation torque. The broken line in the non-dimensional swing torque in each figure shows the cosine curve of the primary rotation component. Therefore, the dimensionless excitation torque in each figure is the difference between the oscillation torque and the rotation primary component. In comparison between FIG. 7 and FIG. 9 as well as in comparison between FIG. 8 and FIG. 10, the positive displacement machine 20 of the embodiment has a smaller excitation torque than the positive displacement machine 920. I understand.

According to the positive displacement machine 20 of the embodiment described above, the

second arm portions

54a and 54b formed as inner circumferential cylindrical surfaces having an axis parallel to the rotation axis of the

shaft members

50a and 50b as a central axis, The

first arm portions

44a and 44b are supported so that the spherical centers P1a and P1b of the outer peripheral

spherical surface portions

45a and 45b attached to the

first arm portions

44a and 44b are constrained on the central axis of the

second arm portions

54a and 54b. As a result, the excitation torque for exciting the surroundings can be reduced as compared with the positive displacement machine 920 of the conventional example. As a result, by shortening the arm length of the

first arm portions

44a and 44b, the swing piece amplitude angle (maximum swing angle) is increased, and by reducing the diameter (bore diameter) of the

pistons

42a and 42b, the piston Even if the stroke increases and the swing piece amplitude angle (maximum swing angle) increases, the excitation torque can be reduced as compared with the positive displacement machine 920 of the conventional example. Miniaturization and efficiency can be achieved. As a result, a smaller, more efficient and lower vibration positive displacement machine can be obtained.

In the positive displacement machine 20 of the embodiment, the outer peripheral

spherical surface portions

45a and 45b are formed or attached and fixed to the

first arm portions

44a and 44b. However, as illustrated in the first modified example of FIG. The outer peripheral spherical surface portion 145a may be rotatably held around the arm axis by the portion 144a. FIG. 11A shows the state of top dead center (rocking angle 0 degree) from the same direction as FIG. 1, and FIG. 11B shows the maximum rocking angle (rocking piece amplitude angle θmax). The state at the time is seen from above in FIG. In this case, as shown in the figure, the portion to which the outer peripheral spherical portion 145a of the first arm portion 144a is attached is formed in a cylindrical shape with the arm axis as the central axis, and the inner peripheral surface of the outer peripheral spherical portion 145a is formed in a cylindrical shape. A roller 146a is interposed between the outer peripheral spherical surface portion 145a and the first arm portion 144a so that the outer peripheral spherical surface portion 145a is rotatable around the arm axis, while a thrust washer 147a is provided on both end surfaces of the outer peripheral spherical surface portion 145a in the arm axis direction. , 148a may be attached to restrict movement of the outer peripheral spherical surface portion 145a in the arm axis direction. If it carries out like this, durability can be improved by rolling between the outer peripheral spherical surface part 145a which is a line contact part, and the internal peripheral surface of the 2nd arm part 54a, and a mechanical friction loss can be made small.

In the positive displacement machine 20 of the embodiment, the outer peripheral

spherical surface portions

45a and 45b of the

first arm portions

44a and 44b are slidably held by the

second arm portions

54a and 54b formed as inner peripheral cylindrical surfaces. As exemplified in the second modification of FIG. 12, the outer peripheral spherical surface 45a of the first arm portion 44a may be supported by the second arm portion 154a via the inner peripheral spherical surface portion 155a. 12A shows the state of the top dead center (rocking angle 0 degree) from the same direction as FIG. 1, and FIG. 12B shows the maximum rocking angle (rocking piece amplitude angle θmax). The state at the time is seen from above in FIG. In this case, the outer peripheral cylindrical surface of the inner peripheral spherical surface portion 155a is slidably held in the circumferential direction and the arm axial direction by the inner peripheral cylindrical surface of the second arm portion 154a, and the first arm portion is supported by the inner peripheral spherical surface portion 155a. The outer peripheral spherical surface portion 45a of 44a may be held by a spherical pair. In this way, since the outer peripheral spherical surface portion 45a is held by the inner peripheral spherical surface portion 155a, the force transfer between the first arm portion 44a and the second arm portion 154a can be performed by surface contact, and the durability in the support structure can be improved. Can be improved. Combining the contents of the first modification described above with the second modification results in the third modification shown in FIG. FIG. 13A shows the state of top dead center (swing angle 0 degree) from the same direction as FIG. 1, and FIG. 13B shows the maximum swing angle (swing piece amplitude angle θmax). The state at the time is seen from above in FIG. Thus, when the first modification and the second modification are combined to form the third modification, the mechanical friction loss is small, and the durability of the support structure can be further improved.

In the second modified example of FIG. 12 and the third modified example of FIG. 13, the end surfaces of the inner peripheral spherical surface portion 155a on the

first arm portions

44a and 144a side are parallel to a plane orthogonal to the rotation axis of the shaft shaft 50a. As shown in the fourth modification of FIG. 14, the end surface of the inner peripheral spherical surface portion 255a is arranged so that the inner peripheral side around the rotation axis of the shaft member 50a is separated from the first arm portion 144a from the outer peripheral side. It is good also as what forms by the slanting slope with respect to a rotating shaft. FIG. 14A shows the state of top dead center (rocking angle 0 degree) from the same direction as FIG. 1, and FIG. 14B shows the maximum rocking angle (rocking piece amplitude angle θmax). The state at the time is seen from above in FIG. In the fourth modification, the inner circumferential spherical portion 255a can move in the axial direction with respect to the inner circumferential cylindrical surface of the second arm portion 254a, but the inner circumferential spherical portion 255a cannot be rotated around its central axis. It is attached to the circumferential cylindrical surface. This attachment can be performed, for example, by spline fitting that allows the inner circumferential cylindrical surface and the inner circumferential spherical surface portion 255a to slide in the axial direction. Thus, by forming the end surface of the inner peripheral spherical surface portion 255a with a slope, the shaft of the first arm portion 144a and the inner peripheral spherical surface portion 255a when the maximum swing angle (at the swing piece amplitude angle) is reached. It is possible to suppress contact and interference with the inner peripheral side around the rotation axis, and the maximum swing angle of the reciprocating member 40 can be further increased. Here, in the fourth modification, the end surface of the inner peripheral spherical surface portion 255a is formed by a slope, but only the portion of the end surface of the inner peripheral spherical surface portion 255a that abuts and interferes with the first arm portion 44a. It is good also as what forms so that it may leave | separate. In the fourth modification, the end surface of the inner peripheral cylindrical surface of the second arm portion 254a on the first arm portion 144a side is formed by a slope like the inner peripheral spherical surface portion 255a, but the rotation of the shaft 50a It may be formed so as to be parallel to a plane orthogonal to the axis.

In the positive displacement machine 20 of the embodiment, the outer peripheral

spherical surface portions

45a and 45b are formed or fixed to the

first arm portions

44a and 44b. However, as illustrated in the fifth modification example of FIG. The outer peripheral spherical surface portion 355a may be attached to the portion 354a. FIG. 15A shows the state of the top dead center (swing angle 0 degree) from the same direction as FIG. 1, and FIG. 15B shows the maximum swing angle (swing piece amplitude angle θmax). The state at the time is seen from above in FIG. In this case, the second arm portion 354a is formed as the outer peripheral cylindrical surface, and the outer peripheral spherical surface portion 355a of the inner peripheral cylindrical surface is slidably held in the arm axis direction of the second arm portion 354a on the second arm portion 354a. The inner spherical surface portion 346a that rotatably holds the spherical surface portion 355a may be attached by an attachment member 345a so as not to move in the arm axis direction of the first arm portion 344a. Even in the fifth modification, the ball center P1a (specific point P1a) is movably restrained on an axis parallel to the rotation axis of the shaft member 50a, that is, on the central axis of the second arm portion 354a. An effect similar to that of the positive displacement machine 20 of the example is achieved. In this case, as exemplified in the sixth modification of FIG. 16, the outer periphery of the inner peripheral spherical surface portion 446a in the first arm portion 444a is formed to be a cylindrical surface, and the outer peripheral surface of the inner peripheral spherical surface portion 446a and the mounting member A roller 447a may be interposed between the inner peripheral surface of 445a and the first spherical arm portion 444a may be freely rotatable around the arm axis. 16A shows the state of top dead center (rocking angle 0 degree) viewed from the same direction as FIG. 1, and FIG. 16B shows the maximum rocking angle (oscillation piece amplitude angle). The state at the time of θmax) is viewed from above in FIG.

In the positive displacement machine 20 of the embodiment, the outer peripheral

spherical surface portions

45a and 45b are formed or attached and fixed to the

first arm portions

44a and 44b, and the outer peripheral

spherical surface portions

45a and 45b are formed by the inner peripheral cylindrical surfaces of the

second arm portions

54a and 54b. Although it is assumed to be slidably held, the outer peripheral spherical surface portion may not be used as illustrated in the seventh modification of FIG. FIG. 17A shows the state of the top dead center (rocking angle 0 degree) from the same direction as FIG. 1, and FIG. 17B shows the maximum rocking angle (rocking piece amplitude angle θmax). The state at the time is seen from above in FIG. FIG. 18 is a cross-sectional view showing the AA cross section of FIG. In the seventh modification, the second arm portion 554a is formed to be an inner peripheral cylindrical surface. The first arm portion 544a is formed or fixed by a substantially barrel-shaped hinge portion 545a having two planes perpendicular to the reciprocating direction of the reciprocating member 40 (the vertical direction in FIG. 1 and the vertical direction in FIG. 17A). The cylindrical annular cylindrical member 548a is slidably disposed on the inner peripheral cylindrical surface of the second arm portion 554a, and slidably contacts two planes of the hinge portion 545a and is integrated with the cylindrical member 548a. And a pair of sliding members 546a. The pair of sliding members 546a can swing around the pin 547a penetrating the central axis with respect to the hinge portion 545a, but the cylindrical member 548a cannot move in the central axis direction. The both ends are supported by a pair of retaining rings 549a. In the support structure of the seventh modified example, the hinge portion 545a formed or attached and fixed to the first arm portion 544a can swing with respect to the cylindrical member 548a using the pin 547a as a swing shaft, and the cylindrical member Since 485a is slidable around the arm axis with respect to the inner peripheral cylindrical surface of the second arm portion 554a, the hinge portion 545a has a specific point P1a at the center (the center of the pin 547a) at the rotation of the shaft member 50a. Although it is constrained to be movable on an axis parallel to the axis (on the central axis of the second arm portion 554a), it can freely rotate and swing with respect to the second arm portion 554a. Similarly to 20, the reciprocating motion accompanying the reciprocating motion of the reciprocating member 40 can perform the revolving motion while being held by the second arm portion 554a. Therefore, the seventh modified example can achieve the same effects as the positive displacement machine 20 of the embodiment.

As in each of these modifications, the support structure of the first arm portion by the second arm portion is constrained so that the specific point specified in advance of the first arm portion can move on an axis parallel to the rotation axis of the shaft member. Any support structure may be used as long as it is suitable.

In the positive displacement machine 20 of the embodiment and its modifications, the

shaft members

50a and 50b are reciprocatingly driven by the pair of

electric motors

70a and 70b attached to the pair of shaft members 50a and 50b. 40 is a machine (compressor) that causes reciprocating motion and swinging motion to cause volume changes of the working chambers 62a and 62b. However, the reciprocating member 40 is supplied by supplying pressure fluid to the working chambers 62a and 62b. It is good also as a machine (engine) which produces a rotational drive force in a pair of

shaft members

50a and 50b by producing a reciprocating motion and a rocking motion.

In the positive displacement machine 20 of the embodiment and the modification thereof, the pair of

pistons

42a and 42b and the pair of working chambers 62a and 62b are provided. However, it is assumed that a single piston and a single working chamber are provided. There is no problem.

As mentioned above, although the form for implementing this invention was demonstrated using the Example, this invention is not limited at all to such an Example, In the range which does not deviate from the summary of this invention, it is with various forms. Of course, it can be implemented.

The present invention can be used in the manufacturing industry of positive displacement machines.

Claims

A cylindrical guide cylindrical member;
A piston portion that is guided by the inner peripheral surface of the guide cylindrical member and reciprocates in the direction of the central axis of the guide cylindrical member and swings around the central axis, and is orthogonal to the central axis of the guide cylindrical member and the central axis A reciprocating member having a pair of first arm parts attached to the piston part so as to be symmetrical with respect to
A pair of shaft members disposed so as to be orthogonal to the central axis of the guide cylindrical member and symmetrical with respect to the central axis;
A pair of second arm portions attached to the pair of shaft members so as to support the pair of first arm portions at positions displaced from the rotation axes of the pair of shaft members,
A working chamber in which a volume change occurs as the piston part reciprocates;
A positive displacement machine comprising:
The second arm portion supports the specific point predetermined in the first arm portion so as to be movably restrained on an axis parallel to the rotation axis of the shaft member.
A positive displacement machine characterized by that.
The positive displacement machine according to claim 1, wherein
The first arm portion has an outer peripheral spherical surface portion having a spherical center as the specific point,
The second arm portion has an inner cylindrical portion that is disposed on an axis parallel to the rotation axis of the shaft member and holds the outer peripheral spherical portion slidably.
Positive displacement machine.
The positive displacement machine according to claim 1, wherein
The first arm portion has an outer peripheral spherical surface portion having a spherical center as the specific point,
The second arm portion includes an inner peripheral spherical surface portion that holds the outer peripheral spherical surface portion and moves on an axis parallel to the rotation axis of the shaft member.
Positive displacement machine.
The positive displacement machine according to claim 3, wherein
The inner peripheral spherical portion has an outer periphery formed in a cylindrical shape,
The second arm portion includes an inner circumferential cylindrical portion that holds the inner circumferential spherical portion movably on an axis parallel to the rotation axis of the shaft member.
Positive displacement machine.
The positive displacement machine according to claim 4, wherein
The inner circumferential spherical portion is formed such that the inner circumferential side around the rotation axis of the shaft member is separated from the first arm portion from the outer circumferential side,
The inner circumferential cylindrical portion holds the inner circumferential spherical portion in a non-rotatable manner around an axis parallel to the rotation axis of the shaft member.
Positive displacement machine.
A positive displacement machine according to any one of claims 2 to 5,
The outer peripheral spherical surface portion is supported so as to be rotatable about the central axis of the first arm portion and immovable in the central axis direction.
Positive displacement machine.
The positive displacement machine according to claim 1, wherein
The first arm portion has an inner circumferential spherical surface portion having a spherical center as the specific point,
The second arm portion has an outer peripheral spherical surface portion that is held on the inner peripheral spherical surface portion and is movable on an axis parallel to the rotation axis of the shaft member.
Positive displacement machine.
The positive displacement machine according to claim 7, wherein
The inner peripheral spherical surface portion is supported so as to be rotatable around the central axis of the first arm portion and immovable in the central axis direction.
Positive displacement machine.
The positive displacement machine according to claim 1, wherein the second arm portion is formed as an inner peripheral cylindrical surface,
The first arm portion has a substantially barrel-shaped hinge portion having two planes perpendicular to the reciprocating direction of the reciprocating member, and is slidably in contact with the two planes of the hinge portion and the second arm portion. And a sliding portion that is slidably in contact with the inner peripheral cylindrical surface of the first hinge portion and that is integrated with the hinge portion by a pin disposed on a central axis of the hinge portion.
A positive displacement machine according to any one of claims 1 to 9,
The piston part has two pistons symmetrically across the pair of first arm parts,
Two working chambers are formed to correspond to each of the two pistons,
Positive displacement machine.