JP2015222037A - Fluid machine - Google Patents
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Abstract
Description
本発明は、流体機械の分野に関するものであり、特に、正味スループット（機械の正味吐出量、又は正味吸入量）を制御する流体機械に関するものである。 The present invention relates to the field of fluid machines, and more particularly to a fluid machine that controls net throughput (net discharge amount or net suction amount of a machine).
流体機械は一般的に、二つの異なる圧力の流体間で作動を行うため、高圧又は低圧の流体を供給及び／又は排出する高圧マニホルドと低圧マニホルドを要する。尚、流体機械には、ポンプ、モータ及び、異なる動作モードによりポンプ又はモータの何れかとして機能することができる機械等の、流体被駆動式及び／又は流体駆動式の機械が含まれる。流体機械がポンプとして作動する場合は、作動室に低圧マニホルドから流体を供給し、昇圧後の流体が高圧マニホルドへ流体が排出され、モータとして作動する場合は、高圧マニホルドから流体が供給され、低圧マニホルドへ流体が排出されるものが一般的に存在している。 Fluidic machines typically operate between two different pressure fluids and therefore require high and low pressure manifolds that supply and / or discharge high or low pressure fluids. It should be noted that fluid machines include fluid driven and / or fluid driven machines such as pumps, motors and machines that can function as either pumps or motors with different modes of operation. When the fluid machine operates as a pump, the fluid is supplied from the low-pressure manifold to the working chamber, and the fluid after pressure increase is discharged to the high-pressure manifold. When the fluid machine operates as a motor, the fluid is supplied from the high-pressure manifold. There is generally something that drains fluid to the manifold.
このような機械の従来技術として、容積が周期的に変化する作動室を複数備え、作動室を通じた流体の排除量が電子制御弁によりサイクル毎に作動室の容積のサイクルと同相の関係で調整されることにより、機械を通じた流体の正味スループットを決定する流体機械が知られている。 As a conventional technology of such a machine, it has multiple working chambers whose volumes change periodically, and the amount of fluid discharged through the working chambers is adjusted in an in-phase relationship with the cycle of the working chamber volume for each cycle by an electronic control valve. In doing so, fluid machines are known that determine the net throughput of fluid through the machine.
例えば、特許文献１では、電子制御ポペット弁を作動室の容積のサイクルと同相の関係で解放及び／又は閉鎖することで、ポンプの各作動室と低圧マニホルドとの間の流体の連通を調整することにより、複数の作動室を通じた流体の（合計の）正味吐出量を制御する方法が公開されている。その結果、各々の作動室が（あらかじめ固定された）所定体積の流体を排除するか、又は流体の正味排除量を伴わないアイドル状態を経るかを、コントローラによりサイクル毎に選択可能にし、ポンプの正味吐出量を要求される負荷に一致されることを可能とする。 For example, in Patent Document 1, fluid communication between each working chamber of the pump and the low-pressure manifold is adjusted by releasing and / or closing an electronically controlled poppet valve in phase with the working chamber volume cycle. Thus, a method for controlling the (total) net discharge amount of fluid through a plurality of working chambers is disclosed. As a result, it is possible for the controller to select, on a cycle-by-cycle basis, whether each working chamber eliminates a predetermined volume of fluid (pre-fixed) or goes through an idle state without a net displacement of fluid. The net discharge amount can be matched with the required load.
さらに、特許文献２では、この原理を発展し、各々の作動室と高圧マニホルドとの間の流体の連通を調整する電子制御ポペットバルブを設けることで、異なる動作モードによりポンプ又はモータの何れかとして機能する流体機械の提供を容易にしている。 Furthermore, Patent Document 2 develops this principle and provides an electronically controlled poppet valve that adjusts fluid communication between each working chamber and the high-pressure manifold, so that it can be used as either a pump or a motor depending on different operation modes. It makes it easy to provide a functional fluid machine.
上記従来技術の原理を用いた流体機械は、各々の作動室と低圧マニホルド又は高圧マニホルド間にそれぞれ電子制御弁などを設ける。したがって、大容量化等を目的に、作動室の数を増大させた際には、作動室の数に対応して、電子制御弁の数も増大する。電子制御弁は、電力を消費する電子制御機構（例えばソレノイドコイルと永久磁石を組み合わせたもの等）を備えるため、電子制御弁の個数が増大するに伴い、例えば消費する電力が増大する可能性がある。これは電子制御弁の場合であるが、電子制御弁に関らず、制御弁の数を減ずることが出来れば、使用する機器数が減少する等、利点がある。 The fluid machine using the principle of the above prior art is provided with an electronic control valve or the like between each working chamber and a low pressure manifold or a high pressure manifold. Therefore, when the number of working chambers is increased for the purpose of increasing the capacity or the like, the number of electronic control valves increases corresponding to the number of working chambers. Since the electronic control valve includes an electronic control mechanism that consumes electric power (for example, a combination of a solenoid coil and a permanent magnet), for example, as the number of electronic control valves increases, there is a possibility that the consumed electric power may increase. is there. This is the case of an electronic control valve, but there is an advantage that the number of devices to be used is reduced if the number of control valves can be reduced regardless of the electronic control valve.
本発明では、使用する制御弁の数を低減可能な流体機械を提供することを目的とする。 An object of the present invention is to provide a fluid machine that can reduce the number of control valves used.
上記課題を解決するために、本発明に係る流体機械は、低圧マニホルド及び高圧マニホルドと接続されると共に、容積が変化する第１の作動室と、 前記低圧マニホルド及び前記高圧マニホルドと接続されると共に、前記第１の作動室の容積変化とは異なるパターンで容積が変化する第２の作動室と、前記第１の作動室と前記第２の作動室とを連通する連通部と、該連通部に備えられて、該連通部の開度を調節する制御弁と、を備えることを特徴とする。 In order to solve the above problems, a fluid machine according to the present invention is connected to a low-pressure manifold and a high-pressure manifold, and is connected to a first working chamber whose volume changes, and to the low-pressure manifold and the high-pressure manifold. A second working chamber whose volume changes in a pattern different from the volume change of the first working chamber, a communicating portion that communicates the first working chamber and the second working chamber, and the communicating portion And a control valve that adjusts the opening degree of the communication portion.
本発明によれば、使用する制御弁の数を低減可能な流体機械を提供することが可能になる。 According to the present invention, it is possible to provide a fluid machine that can reduce the number of control valves to be used.
以下、本発明を実施する上で好適な実施例について説明する。下記実施例では、容積変化量が等しく、かつ互いに逆位相で容積変化する作動室１と作動室２を連通し、その間に制御弁を有する場合を特に説明している。そして、制御弁を調整することにより作動室１と作動室２の間の流体のやり取りの量（以下、制御弁流量と記す）と、低圧マニホルド又は高圧マニホルドとの流体のやり取りの量を制御することができる様にしている。尚、容積変化量が等しく、かつ互いに逆位相で容積変化する作動室１と作動室２は、ある一定時間での、各作動室の互いの吐出量及び吸入量を等しくできる。 Hereinafter, preferred examples for carrying out the present invention will be described. In the following embodiment, a case is described in which the working chamber 1 and the working chamber 2 having the same volume change amount and volume changes in opposite phases are communicated and a control valve is provided between them. Then, the amount of fluid exchange between the working chamber 1 and the working chamber 2 (hereinafter referred to as control valve flow rate) and the amount of fluid exchange with the low pressure manifold or the high pressure manifold are controlled by adjusting the control valve. I am trying to do that. Note that the working chamber 1 and the working chamber 2 having the same volume change amount and volume changes in opposite phases can have the same discharge amount and suction amount of each working chamber in a certain time.
例えば、制御弁流量がゼロでない場合、作動室１と作動室２は容積変化量が等しく、かつ互いに逆位相で容積変化するため、互いの作動室の吐出量及び吸入量は等しく、制御弁を通過する流体は容積変化に伴う仕事を受けることなく、各作動室の容積の周期的変化に伴って、作動室１と作動室２の間で流体が往来する。そして制御弁流量分だけ、各作動室と低圧マニホルド又は高圧マニホルドとの流体のやり取りの量が減少するため、正味スループットを制御することができる。 For example, if the flow rate of the control valve is not zero, the working chamber 1 and the working chamber 2 have the same volume change amount, and the volume changes in opposite phases to each other. The passing fluid does not receive work due to the volume change, and the fluid moves between the working chamber 1 and the working chamber 2 as the volume of each working chamber changes periodically. Since the amount of fluid exchange between each working chamber and the low pressure manifold or the high pressure manifold is reduced by the control valve flow rate, the net throughput can be controlled.
即ち、複数の作動室に１つの制御弁で正味スループットを制御できるため、同じ作動室の数で、かつ最大正味スループットが同じ流体機械であれば、従来技術に比して少なくとも制御弁の数を半減することができる。 That is, since the net throughput can be controlled by a single control valve in a plurality of working chambers, if the number of working chambers is the same and the maximum net throughput is the same fluid machine, at least the number of control valves is reduced as compared with the prior art. Can be halved.
上記は、本発明を実施する上で特に好適となる実施態様であるが、容積変化量が等しく、かつ互いに逆位相で容積変化する複数の作動室間を連通し、その間に連通部の開度を調節し、連通部に流れる流体の量を調節する制御弁を備える場合のみならず、１の作動室の容積変化とは異なるパターン（例えば、容積変化の周期は同じだが位相が異なる場合や、周期がそもそも異なる場合などが挙げられる。）で容積が変化する別の作動室を備え、両作動室間を連通し、その間に連通部の開度を調節し、連通部に流れる流体の量を調節する制御弁を備える様にすればよい。これによっても複数の作動室につき１つの制御弁を用いることで足り、制御弁の数を減ずることが可能である。 The above is an embodiment that is particularly suitable for carrying out the present invention. However, the plurality of working chambers having the same volume change amount and changing in volume in opposite phases communicate with each other, and the opening degree of the communication portion therebetween. In addition to the case where a control valve for adjusting the amount of fluid flowing to the communication portion is provided, a pattern different from the volume change of one working chamber (for example, the period of volume change is the same but the phase is different, In the first place, there is another working chamber whose volume changes, and communicates between the two working chambers, and adjusts the opening of the communicating portion between them to control the amount of fluid flowing to the communicating portion. What is necessary is just to provide the control valve to adjust. Also by this, it is sufficient to use one control valve for a plurality of working chambers, and the number of control valves can be reduced.
さらに、互いに同位相で容積変化する作動室１同士を複数連通した作動室群１と、作動室１とは逆位相で、互いには同位相で容積変化する作動室２を連通し、作動室群１と容積変化量を同じにした作動室群２を、作動室群１と作動室群２を連通し、その間に制御弁を設けることにより、上記原理と同様に正味スループットを制御することを可能にする。異なる言い方をすると、作動室群を構成する各作動室の容積及び作動室群を構成する各作動室間の連結部の容積の和は、逆位相の作動室群を構成する各作動室の容積及び作動室群を構成する各作動室間の連結部の容積の和と略同じにしている。この場合、上述の例と同じ作動室の数で、かつ最大正味スループットが同じ流体機械であれば、更に制御弁の数を削減することができる。 Further, a working chamber group 1 in which a plurality of working chambers 1 whose volumes change in the same phase communicate with each other and a working chamber 2 in which the working chambers 1 change in volume in opposite phases and in the same phase communicate with each other. It is possible to control the net throughput in the same manner as in the above principle by connecting the working chamber group 2 having the same volume change amount to 1 and connecting the working chamber group 1 and the working chamber group 2 with a control valve therebetween. To. In other words, the sum of the volume of each working chamber constituting the working chamber group and the volume of the connection portion between each working chamber constituting the working chamber group is the volume of each working chamber constituting the working chamber group in the opposite phase. And the sum of the volumes of the connecting portions between the working chambers constituting the working chamber group. In this case, the number of control valves can be further reduced if the fluid machines have the same number of working chambers as in the above-described example and the same maximum net throughput.
尚、電子制御機構に用いられる永久磁石は、使用されるレアメタルにより高コストになる可能性があり、これに伴って電子制御弁の数が増加すると、装置全体のコスト増加にも繋がる。 The permanent magnet used in the electronic control mechanism may be expensive due to the rare metal used. If the number of electronic control valves increases accordingly, the cost of the entire apparatus will increase.
電子制御弁の数を減らすことで、正味スループットを省電力で制御可能であり、かつコスト増大を抑制した流体機械を提供することも可能になる。 By reducing the number of electronic control valves, it is possible to provide a fluid machine that can control the net throughput with power saving and suppress the increase in cost.
第１の実施形態を図１ないし図４を用いて説明する。本実施例における流体機械は、複数のシリンダとピストンにより容積が周期的に変化する作動室を、回転軸の半径方向に構成した、ラジアルピストン型ポンプである。 A first embodiment will be described with reference to FIGS. The fluid machine in the present embodiment is a radial piston pump in which a working chamber whose volume is periodically changed by a plurality of cylinders and pistons is configured in the radial direction of the rotation shaft.
図１はラジアルピストン型ポンプ１００の回転軸線Ａ１に沿った方向の断面図である。図２は、本実施例におけるラジアルピストン型ポンプ１００を、図１に示すＡ−Ａ’断面で、回転軸線Ａ１に垂直な平面で切断した断面図である。 FIG. 1 is a cross-sectional view of the radial piston pump 100 in the direction along the rotational axis A1. FIG. 2 is a cross-sectional view of the radial piston pump 100 according to the present embodiment cut along a plane perpendicular to the rotation axis A1 in the A-A ′ cross section shown in FIG. 1.
図１、図２に示すラジアルピストン型ポンプ１００は、作動室１０８の容積を周期的に変化させるための装置として、複数の凸部と凹部とを滑らかに（傾きが不連続にならない、或いは角を備えていないとも言える。）連続されたカム面を持つカムリング１０１と、カム面に対して追従し、カム面の表面を転動して回転するローラー１０５と、各ローラーに取り付けられて凹部または凸部の凹凸方向に駆動するピストン１０６を備えている。ローラーは回転軸の回転により、回転軸の周囲を回転する。 The radial piston pump 100 shown in FIG. 1 and FIG. 2 is a device for periodically changing the volume of the working chamber 108, and smoothly has a plurality of convex portions and concave portions (the inclination does not become discontinuous, or the angular A cam ring 101 having a continuous cam surface, a roller 105 that follows the cam surface and rolls and rotates on the surface of the cam surface, and a recess or A piston 106 is provided for driving in the direction of protrusions and recesses. The roller rotates around the rotation axis by the rotation of the rotation axis.
カムリング１０１と、内側部材１０２は前記回転軸線Ａ１を回転軸として相対回転する。本実施例では、内側部材１０２と外側部材１０３は回転軸線Ａ１に対して回転不能に固定し、カムリング１０１と接続部材１０４は、キーやスプラインなどで互いに固定されており、接続部材１０４に動力源が接続されることにより、カムリング１０１と接続部材１０４が回転軸線Ａ１に対して回転する。接続部材１０４は、内部部材１０２に、軸受１１２を通じて回転可能に支持される。 The cam ring 101 and the inner member 102 rotate relative to each other about the rotation axis A1. In this embodiment, the inner member 102 and the outer member 103 are fixed so as not to rotate with respect to the rotation axis A1, and the cam ring 101 and the connecting member 104 are fixed to each other with a key, a spline, or the like. As a result, the cam ring 101 and the connecting member 104 rotate with respect to the rotation axis A1. The connecting member 104 is rotatably supported by the inner member 102 through a bearing 112.
内側部材１０４は、シリンダ１０７を備えており、ピストン１０６とシリンダ１０７に囲まれた空間が作動室１０８となる。なお、図１では、簡単のため接続部材１０４の一部を省略している。 The inner member 104 includes a cylinder 107, and a space surrounded by the piston 106 and the cylinder 107 serves as a working chamber 108. In FIG. 1, a part of the connection member 104 is omitted for simplicity.
カムリング１０１と、内側部材１０２の相対回転により、ローラー１０５が、周期的な凸部と凹部をもつカムリング１０１のカム面を転動し、ローラー１０５に取り付けられたピストン１０６が、シリンダ１０７内で往復運動を行うことにより、作動室１０８の容積が周期的に変化する。 By the relative rotation of the cam ring 101 and the inner member 102, the roller 105 rolls on the cam surface of the cam ring 101 having periodic convex portions and concave portions, and the piston 106 attached to the roller 105 reciprocates in the cylinder 107. By performing the movement, the volume of the working chamber 108 changes periodically.
なお、ローラー、ピストン、シリンダ、作動室は周方向に複数存在し、それぞれ区別が必要な場合は、例えば作動室１０８ａの様に、アルファベットを付記する（図２）。 Note that there are a plurality of rollers, pistons, cylinders, and working chambers in the circumferential direction, and in the case where distinction is necessary, alphabets are added, for example, like the working chamber 108a (FIG. 2).
作動室１０８は、外側部材１０３の全周に渡って設けられた高圧マニホルド１０９と低圧マニホルド１１０に接続されており、低圧マニホルド１０９に作動油が外部から供給され、昇圧された作動流体が高圧マニホルド１１０から外部へ排出される接続口を有している（図示していない）。ここでは、昇圧されていないものを低圧、昇圧されているものを高圧と呼んでいる。 The working chamber 108 is connected to a high-pressure manifold 109 and a low-pressure manifold 110 provided over the entire circumference of the outer member 103, and hydraulic oil is supplied to the low-pressure manifold 109 from the outside, and the pressurized working fluid is supplied to the high-pressure manifold. It has a connection port that is discharged from 110 to the outside (not shown). Here, those that are not boosted are called low pressure, and those that are boosted are called high pressure.
作動室１０８各マニホルドへの接続を選択する整流器として、逆止弁１１１を備えており、作動室１０８から高圧マニホルド１０９へと、低圧マニホルド１１０から作動室１０８への方向に、接続を制限する。逆止弁は、入口と出口の差圧がある設定圧力になると、ある方向にだけ流体を流す弁である。なお、高圧マニホルドに接続されている逆止弁を逆止弁１１１Ｈ、低圧マニホルドに接続されている逆止弁を逆止弁１１１Ｌと記す。 A check valve 111 is provided as a rectifier for selecting connection to each manifold of the working chamber 108, and the connection is restricted in the direction from the working chamber 108 to the high-pressure manifold 109 and from the low-pressure manifold 110 to the working chamber 108. The check valve is a valve that allows a fluid to flow only in a certain direction when a differential pressure between the inlet and the outlet reaches a set pressure. The check valve connected to the high pressure manifold is referred to as a check valve 111H, and the check valve connected to the low pressure manifold is referred to as a check valve 111L.
図２に示すように、本実施例では、カムリング１０１は６個のカムローブ（カムの凸凹）を有しており、π／３ラジアン回転すると、カム面の変動が１周期する。カム面の変動１周期当たりの角度をＴ（ラジアン）とすると、１つ目の作動室に対して、Ｔ／２＋Ｎ×Ｔラジアン（Ｎは整数）の位置に２つ目の作動室を配置すると、それらの容積を変化させるピストンの往復運動は逆位相になる。本構成では、π／４ラジアンごとに８個の作動室１０８（１０８ａ〜１０８ｈ）を有しており、この場合はπ／２ラジアン角度が異なって配置された作動室同士の容積変化が逆位相となる。例えば、図２中の作動室１０８ａと１０８ｃ、作動室１０８ｂと１０８ｄ、作動室１０８ｅと１０８ｇ、作動室１０８ｆと１０８ｈがそれぞれ互いに逆位相で容積が変化する。本実施例では図２中の破線で示すように、これら逆位相の作動室を連通させる。実際は内側部材１０２の内部に連通するための流路を設けるが、図２では簡便のため破線で連通を表す。さらに、互いに逆位相で容積が変化作動室の間に、制御弁１１３（１１３ａ〜１１３ｄ）を備える。制御弁１１３は開度によって作動室間の連通部を往来する流体の流量を調節する。制御弁１１３は、最大で各作動室から吐出される最大流量を、高圧マニホルド１０９との間に設けられた逆止弁１１１Ｈの設定圧力よりも小さい圧力差で流せるものを用いる。 As shown in FIG. 2, in this embodiment, the cam ring 101 has six cam lobes (cam irregularities), and the cam surface fluctuates by one cycle when rotated by π / 3 radians. When the angle per cam cycle variation is T (radian), the second working chamber is arranged at a position of T / 2 + N × T radians (N is an integer) with respect to the first working chamber. The reciprocating motions of the pistons that change their volume are in opposite phases. In this configuration, eight working chambers 108 (108a to 108h) are provided for every π / 4 radians. In this case, volume changes between working chambers arranged at different π / 2 radians are in reverse phase. It becomes. For example, the volumes of the working chambers 108a and 108c, the working chambers 108b and 108d, the working chambers 108e and 108g, and the working chambers 108f and 108h in FIG. In the present embodiment, as shown by the broken line in FIG. Actually, a flow path for communicating with the inside of the inner member 102 is provided. In FIG. Further, control valves 113 (113a to 113d) are provided between the working chambers whose volumes change in opposite phases to each other. The control valve 113 adjusts the flow rate of the fluid that passes through the communication portion between the working chambers according to the opening degree. As the control valve 113, a valve that can flow a maximum flow rate discharged from each working chamber at a pressure difference smaller than a set pressure of the check valve 111 </ b> H provided between the high-pressure manifold 109 is used.
次に本実施例に関する可変容量機構について図３及び図４を用いて説明する。
図３は、本発明に関わる可変容量の動作を説明するために、容積変化量が等しく（等しいとは、厳密に等しい必要はなく、実質的に等しければ足りる。略等しいと表現した場合は、実質的に等しいことをより明確にしたものであるが、略がなくても実質的に等しいことを同様に指す。以下同様である。）かつ互いに逆位相で（こちらも厳密に逆位相である必要はなく、実質的に逆位相であれば足りる。略逆位相と表現した場合は、実質的に逆位相となることをより明確にしたものであるが、略がなくても実質的に逆位相であることを同様に指す。同位相の場合も同様である。以下同様である。）容積変化する作動室と、制御弁とに注目して示した図である。また、作動室１と作動室２の容積変化の周囲も等しい。
Next, the variable capacity mechanism according to this embodiment will be described with reference to FIGS.
FIG. 3 is a diagram illustrating the operation of the variable capacity according to the present invention. Although it is more clear that it is substantially equal, it also means that it is substantially equal even if there is no omission, and so on. It is not necessary, and it is sufficient if the phase is substantially reversed. Similarly, in the case of the same phase, the same applies hereinafter.) It is a view showing the working chamber whose volume changes and the control valve. Moreover, the circumference of the volume change of the working chamber 1 and the working chamber 2 is also equal.
本実施例では、図３と同様の動作をする逆位相の作動室の組が４組あり、そのうち、図２における作動室１０８ａと作動室１０８ｃの関係を示している。図４は、図３に示す作動室の容積変化（ピストンの動き）と、低圧マニホルドと高圧マニホルドとの流体のやり取りの量（すなわち正味スループットの量）と、制御弁の開度の関係を示している。 In this embodiment, there are four sets of working chambers of opposite phases that operate in the same manner as in FIG. 3, and the relationship between the working chamber 108a and the working chamber 108c in FIG. 2 is shown. FIG. 4 shows the relationship between the change in volume of the working chamber (piston movement) shown in FIG. 3, the amount of fluid exchange between the low pressure manifold and the high pressure manifold (ie, the amount of net throughput), and the opening of the control valve. ing.
図３では、作動室１０８ａが最大容量の状態（上死点）であり、作動室１０８ｃが最小容量の状態（下死点）である。先ず制御弁が閉じている場合は、図中矢印の方向にカム面が動くと、それに従って作動室１０８ａは容積が小さくなり、その体積減少分の流体を、逆止弁１１１Ｈを介して高圧マニホルド１０９に吐出する。一方で作動室１０８ｃは作動室が膨張するに従って、逆止弁１１１Ｌを介して低圧マニホルド１１０から流体を吸入する。この時のそれぞれの作動室におけるピストンの動きと、吐出・吸入量を図４−１と図４−３に示す。制御弁１１３ａは、閉じているので、図４−２の太線で示すように、この時の制御弁流量はゼロである。 In FIG. 3, the working chamber 108a has a maximum capacity (top dead center), and the working chamber 108c has a minimum capacity (bottom dead center). First, when the control valve is closed, when the cam surface moves in the direction of the arrow in the figure, the volume of the working chamber 108a decreases accordingly, and the reduced volume of fluid is supplied to the high pressure manifold via the check valve 111H. It discharges to 109. On the other hand, the working chamber 108c sucks fluid from the low pressure manifold 110 through the check valve 111L as the working chamber expands. The movement of the piston and the discharge / suction amount in each working chamber at this time are shown in FIGS. 4-1 and 4-3. Since the control valve 113a is closed, the flow rate of the control valve at this time is zero as shown by the thick line in FIG.
次に、制御弁を全開にした場合は、図４−１〜図４−３に示すように、例えば、作動室１０８ａから吐出される流体は、すべて作動室１０８ｃに流入する。従って、各作動室と、各マニホルド間での流体のやり取りは無い。作動室１０８ａと作動室１０８ｃの容積変化が逆位相で行われるため、吐出する流体と、吸入する流体量が同じとなり、少ない損失で、作動室と各マニホルド間とのやり取りをゼロにできる。このように、制御弁１１３ａを全開にすることで、正味スループットの量をゼロにすることができ、機械のアイドル状態を実現することができる。 Next, when the control valve is fully opened, as shown in FIGS. 4-1 to 4-3, for example, all the fluid discharged from the working chamber 108a flows into the working chamber 108c. Therefore, there is no fluid exchange between each working chamber and each manifold. Since the volume changes of the working chamber 108a and the working chamber 108c are performed in opposite phases, the amount of fluid to be discharged and the amount of fluid to be sucked are the same, and exchange between the working chamber and each manifold can be made zero with little loss. Thus, by fully opening the control valve 113a, the amount of net throughput can be made zero, and the idle state of the machine can be realized.
最後に、制御弁１１３ａの開度を半開に調節した場合は、図４−１、図４−２、図４−３の細かい破線で示すように、ピストン１０６ａが上死点から下死点へ変化する際に、作動室１０８ａから吐出される流体の一部が、作動室１０８ｃへ流入する。なお、図４−２の“ａ→ｃ”は、図３の制御弁１１３ａの左右に示している“ａ”から“ｃ”の方向へ流れる流量を表しており、“ｃ→ａ”は逆方向へ流れる流量を表している。この時、図４−１、図４−３に示すように、制御弁１１３ａの流量分だけ、各マニホルドとのやり取りが減少する。 Finally, when the opening degree of the control valve 113a is adjusted to half open, the piston 106a moves from the top dead center to the bottom dead center as shown by the fine broken lines in FIGS. 4-1, 4-2, and 4-3. When changing, a part of the fluid discharged from the working chamber 108a flows into the working chamber 108c. Note that “a → c” in FIG. 4B represents the flow rate flowing from “a” to “c” shown on the left and right of the control valve 113a in FIG. 3, and “c → a” is the opposite. It represents the flow rate flowing in the direction. At this time, as shown in FIGS. 4-1 and 4-3, the exchange with each manifold is reduced by the flow rate of the control valve 113a.
すなわち、制御弁１０３を介して、吐出する流体と、吸入する流体量が同じとなる逆位相の作動室を接続しているために、本来、高圧マニホルド１１０に吐出され、低圧マニホルド１０９から吸入される流体量がキャンセルされ、キャンセルされた流体量だけ、高圧マニホルド１１０又は／及び低圧マニホルド１０９と流体のやり取りの量を減少することができる。したがって、制御弁１１３ａの流量を調整することにより、流体機械の正味スループットの量を可変にすることが可能となる。 In other words, since the discharge fluid and the opposite-phase working chamber having the same amount of fluid to be sucked are connected via the control valve 103, they are originally discharged to the high-pressure manifold 110 and sucked from the low-pressure manifold 109. And the amount of fluid exchange with the high pressure manifold 110 and / or the low pressure manifold 109 can be reduced by the canceled fluid amount. Therefore, the amount of net throughput of the fluid machine can be made variable by adjusting the flow rate of the control valve 113a.
このように、本実施例は容積変化が逆位相の作動室を連通させて組み合わせることにより、各作動室と各マニホルド間で吸入・吐出される流体量を調節しているため、各作動室にそれぞれ制御弁を設ける必要がなくなり、大容量化等を目的に、作動室の数を増大させた際にも、制御弁の数を削減することができる。したがって、制御弁を制御するために消費される電力を削減でき、制御弁のコストを削減することができる。 As described above, in this embodiment, the amount of fluid sucked and discharged between each working chamber and each manifold is adjusted by combining working chambers whose volume changes are in opposite phases to each other. There is no need to provide each control valve, and the number of control valves can be reduced even when the number of working chambers is increased for the purpose of increasing the capacity. Therefore, the power consumed to control the control valve can be reduced, and the cost of the control valve can be reduced.
さらに本発明では、制御弁１１３ａの開度のみを調節することにより、正味スループットを制御できるため、制御性が良い。図３に示すように、負荷に応じて開度を調節するコントローラ１１４は、例えば、入力信号に比例して開度を調節するような、容易な制御を実行できるもので良い。コントローラ１１４は、求められる流体の流量（需要量）に応じて調節しても良いし、機械に入力される動力源が変動する場合は、その大きさに従って（例えば比例して）調節しても良い。またコントローラ１１４は、一つで複数の制御弁を制御しても良い。本実施例ではコントローラ１１４により、制御弁１１３ａ〜１１３ｄを全て制御する構成である。 Furthermore, in the present invention, since the net throughput can be controlled by adjusting only the opening degree of the control valve 113a, the controllability is good. As shown in FIG. 3, the controller 114 that adjusts the opening according to the load may be capable of executing easy control such as adjusting the opening in proportion to the input signal. The controller 114 may be adjusted according to the required flow rate (demand amount) of the fluid, and if the power source input to the machine fluctuates, it may be adjusted according to the magnitude (for example, proportionally). good. The controller 114 may control a plurality of control valves by one. In this embodiment, the controller 114 controls all the control valves 113a to 113d.
実施例２を図２と図５を用いて説明する。実施例２は、実施例１において、連通する作動室を更に増やしたものであり、更なる制御弁の削減を実現するものである。図５は、図２においての同位相の更に別の作動室を各々連結し、その間に制御弁を設けた模式図である。実際は、図２の状態で、接続配管１１５（１１５ａ〜１１５ｄ）を内側部材１０２の内部に設けることにより、作動室を連通する。 A second embodiment will be described with reference to FIGS. In the second embodiment, the number of working chambers communicating with each other is further increased in the first embodiment, and a further reduction in the number of control valves is realized. FIG. 5 is a schematic view in which still another working chamber in the same phase in FIG. 2 is connected and a control valve is provided between them. Actually, in the state shown in FIG. 2, the working chambers are communicated by providing the connecting pipe 115 (115 a to 115 d) inside the inner member 102.
実施例１で示した、図２の様なラジアルピストン型のポンプでは、１回転当たりに複数の凸凹部を持つカム面と、複数のシリンダを組み合わせている。このようなラジアルピストン型の流体機械では、同位相で容積が変化する作動室が複数構成し得る。実際、図２では、作動室１０８ａと作動室１０８ｅは、同位相で容積が変化する。またその他の組み合わせ(作動室１０８ｂと作動室１０８ｆ、作動室１０８ｃと作動室１０８ｇ、作動室１０８ｄと作動室１０８ｈ)も同様に、同位相で容積が変化する。さらに、作動室１０８ａと作動室１０８ｅの二つの作動室と、作動室１０８ｃと作動室１０８ｇの二つの作動室は、逆位相で容積変化する。従って、図５に示すように、まず同位相の作動室を接続配管１１５で連通し、それら連通した作動室群で、さらに逆位相で容積変化する作動室群とを制御弁１１３ｅ、１１３ｆで接続することにより、可変容量制御が可能となり、さらに制御弁の数を削減することができる。 In the radial piston type pump shown in FIG. 2 shown in the first embodiment, a cam surface having a plurality of convex and concave portions per rotation and a plurality of cylinders are combined. In such a radial piston type fluid machine, a plurality of working chambers whose volumes change in the same phase can be formed. In fact, in FIG. 2, the volume of the working chamber 108a and the working chamber 108e changes in phase. Similarly, the volume of other combinations (working chamber 108b and working chamber 108f, working chamber 108c and working chamber 108g, working chamber 108d and working chamber 108h) changes in phase. Further, the volume of the two working chambers 108a and 108e and the two working chambers 108c and 108g change in opposite phases. Therefore, as shown in FIG. 5, first, the working chambers in the same phase are communicated by the connection pipe 115, and the working chamber groups that communicate with each other and the working chamber groups that change in volume in the opposite phase are connected by the control valves 113e and 113f. By doing so, variable displacement control becomes possible, and the number of control valves can be further reduced.
このように、互いに同位相で容積変化する作動室を複数連通した作動室群１と、作動室群１とは逆位相で、互いには同位相で容積変化する作動室を連通し、作動室群１と容積変化量を同じにした作動室群２を、作動室群１と作動室群２を連通し、その間に制御弁を設けることにより、上述の原理と同様に正味スループットを制御することを可能にする。尚、作動室群を構成する作動室の数は２つに限られるものでなく、３つ以上とすることも可能である。この場合、上述の例と同じ作動室の数で、かつ最大正味スループットが同じ流体機械であれば、更に制御弁の数を削減することができる。 As described above, the working chamber group 1 in which a plurality of working chambers whose volumes change in the same phase communicate with each other, and the working chamber group 1 which communicates in a phase opposite to each other and whose volumes change in phase with each other, communicate with each other. It is possible to control the net throughput in the same manner as the above-mentioned principle by connecting the working chamber group 2 having the same volume change amount to 1 and connecting the working chamber group 1 and the working chamber group 2 with a control valve therebetween. to enable. Note that the number of working chambers constituting the working chamber group is not limited to two, and may be three or more. In this case, the number of control valves can be further reduced if the fluid machines have the same number of working chambers as in the above-described example and the same maximum net throughput.
１００ ラジアルピストン型ポンプ
１０１ カムリング
１０２ 内側部材
１０３ 外側部材
１０４ 接続部材
１０５ ローラー
１０６ ピストン
１０７ シリンダ
１０８ 作動室
１０９ 高圧マニホルド
１１０ 低圧マニホルド
１１１ 逆止弁
１１２ 軸受
１１３ 制御弁
１１４ コントローラ
１１５ 接続配管
DESCRIPTION OF SYMBOLS 100 Radial piston type pump 101 Cam ring 102 Inner member 103 Outer member 104 Connecting member 105 Roller 106 Piston 107 Cylinder 108 Working chamber 109 High pressure manifold 110 Low pressure manifold 111 Check valve 112 Bearing 113 Control valve 114 Controller 115 Connection piping
Claims (12)
前記低圧マニホルド及び前記高圧マニホルドと接続されると共に、前記第１の作動室の容積変化とは異なるパターンで容積が変化する第２の作動室と、
前記第１の作動室と前記第２の作動室とを連通する連通部と、
該連通部に備えられて、該連通部の開度を調節する制御弁と、を備えることを特徴とする流体機械。 A first working chamber connected to the low pressure manifold and the high pressure manifold and having a variable volume;
A second working chamber connected to the low pressure manifold and the high pressure manifold and having a volume changing in a pattern different from a volume change of the first working chamber;
A communicating portion that communicates the first working chamber and the second working chamber;
A fluid machine comprising: a control valve provided in the communication part and configured to adjust an opening degree of the communication part.
前記低圧マニホルド及び前記高圧マニホルドと接続されると共に、前記第１の作動室の容積変化とは異なるパターンで容積が変化する第２の作動室と、
前記第１の作動室と前記第２の作動室とを連通する連通部と、
該連通部に備えられて、該連通部に流れる流体の量を調節する制御弁と、を備えることを特徴とする流体機械。 A first working chamber connected to the low pressure manifold and the high pressure manifold and having a variable volume;
A second working chamber connected to the low pressure manifold and the high pressure manifold and having a volume changing in a pattern different from a volume change of the first working chamber;
A communicating portion that communicates the first working chamber and the second working chamber;
A fluid machine comprising: a control valve that is provided in the communication part and adjusts an amount of fluid flowing through the communication part.
前記第１の作動室の容積と前記第２の作動室の容積は略等しいことを特徴とする流体機械。 The fluid machine according to claim 1 or 2,
The fluid machine according to claim 1, wherein the volume of the first working chamber and the volume of the second working chamber are substantially equal.
前記第１の作動室の容積変化における周期と、前記第２の作動室の容積変化における周期とは略同じであることを特徴とする流体機械。 The fluid machine according to any one of claims 1 to 3,
The fluid machine according to claim 1, wherein a cycle in the volume change of the first working chamber and a cycle in the volume change of the second working chamber are substantially the same.
前記第１の作動室の容積変化における位相と、前記第２の作動室の容積変化における位相はずれていることを特徴とする流体機械。 The fluid machine according to claim 4,
The fluid machine characterized in that the phase in the volume change of the first working chamber is shifted from the phase in the volume change of the second working chamber.
前記第１の作動室の容積変化における位相と、前記第２の作動室の容積変化における位相は、互いに略逆位相となることを特徴とする流体機械。 The fluid machine according to claim 5,
The fluid machine according to claim 1, wherein the phase in the volume change of the first working chamber and the phase in the volume change of the second working chamber are substantially opposite to each other.
更に、前記第１の作動室の容積変化と略同位相で変化すると共に、前記第１の作動室と連結される第３の作動室と、
前記第２の作動室の容積変化と略同位相で変化すると共に、前記第２の作動室と連結される第４の作動室と、を備えることを特徴とする流体機械。 The fluid machine according to any one of claims 4 to 6,
And a third working chamber that changes in substantially the same phase as the volume change of the first working chamber and is connected to the first working chamber;
A fluid machine comprising: a fourth working chamber that changes in substantially the same phase as a volume change of the second working chamber and is connected to the second working chamber.
前記第１の作動室の容積、第３の作動室の容積、及び前記第１の作動室と第３の作動室の間の連結部の容積の和と、前記第２の作動室の容積、第４の作動室の容積、及び前記第２の作動室と第４の作動室の間の連結部の容積の和は略同じであることを特徴とする流体機械。 The fluid machine according to claim 7,
The sum of the volume of the first working chamber, the volume of the third working chamber, and the volume of the connecting portion between the first working chamber and the third working chamber, the volume of the second working chamber, The fluid machine characterized in that the sum of the volume of the fourth working chamber and the volume of the connecting portion between the second working chamber and the fourth working chamber is substantially the same.
前記制御弁を制御するコントローラを備えることを特徴とする流体機械。 A fluid machine according to any one of claims 1 to 8,
A fluid machine comprising a controller for controlling the control valve.
更に複数の凸部と凹部とが滑らかに連続されたカム面と、該カム面の表面を転動するローラーと、該ローラーに取り付けられて前記凹部または前記凸部の凹凸方向に駆動するピストンと、該ピストンとの間に前記作動室を形成するシリンダとを備えたことを特徴とする流体機械。 A fluid machine according to any one of claims 1 to 10,
Furthermore, a cam surface in which a plurality of convex portions and concave portions are smoothly continuous, a roller that rolls on the surface of the cam surface, and a piston that is attached to the roller and drives in the concave-convex direction of the concave portion or the convex portion. A fluid machine comprising a cylinder forming the working chamber between the piston and the piston.
更に、自身の回転により、自身の周囲を前記ローラーが回転する様にする回転軸を備えることを特徴とする流体機械。 The fluid machine according to claim 11,
The fluid machine further comprises a rotating shaft that rotates the roller around the rotation of the roller.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014106652A JP2015222037A (en) | 2014-05-23 | 2014-05-23 | Fluid machine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014106652A JP2015222037A (en) | 2014-05-23 | 2014-05-23 | Fluid machine |
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| JP2015222037A true JP2015222037A (en) | 2015-12-10 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| KR20220135676A (en) | 2021-03-31 | 2022-10-07 | 주식회사 신아티앤씨 | Partially epoxy (meta)acrylate resin composition and method for preparing the same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20220135676A (en) | 2021-03-31 | 2022-10-07 | 주식회사 신아티앤씨 | Partially epoxy (meta)acrylate resin composition and method for preparing the same |
| KR20230047978A (en) | 2021-03-31 | 2023-04-10 | 주식회사 신아티앤씨 | Partially epoxy (meta)acrylate resin composition and method for preparing the same |
| KR20230048266A (en) | 2021-03-31 | 2023-04-11 | 주식회사 신아티앤씨 | Partially epoxy (meta)acrylate resin composition and method for preparing the same |
| KR20230048265A (en) | 2021-03-31 | 2023-04-11 | 주식회사 신아티앤씨 | Partially epoxy (meta)acrylate resin composition and method for preparing the same |
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