201033598 六、發明說明： 【發明所屬之技術領域】 本發明是關於以同一裝置能夠測定輪胎之均勻性和動 平衡的輪胎測試機及輪胎測試方法。 【先前技術】 輪胎在生產線的檢查，有輪胎的動平衡測定及均勻性 Φ 測定。該等檢查是使用動平衡測試機及均勻性測試機，分 別使用不同的測試機實施測試。然而，若考量到裝置成本 的削減或生產性（生產量）的提昇時，當然是以同一裝置進 行該等檢查會比較好。於是，對於先前的輪胎測試機，就 開發有以1個裝置能夠進行輪胎之動平衡測定和均勻性測 定的技術。 例如：專利文獻1中，揭示有輪胎之均勻性和動平衡 以1個裝置就能夠測定的均勻性暨動平衡複合測試機。該 Φ 複合測試機是均勻性測試機改造成能夠測定動平衡，具備 有可轉換成低速和高速來旋轉驅動輪胎保持用心軸的旋轉 手段。 該專利文獻1的複合測試機是對輪胎的均句性進行測 定時，構成爲以低速旋轉心軸所保持的輪胎，將形成爲路 面的轉筒推向輪胎藉此測試輪胎的均勻性。另一方面’在 對輪胎的動平衡進行測定時，構成爲將轉筒離開輪胎’以 高速旋轉輪胎，藉此測定輪胎的動平衡。 [先行技術文獻] -5- 201033598 [專利文獻] [專利文獻1]日本特開2004-299673號公報 【發明內容】 [發明欲解決之課題] 專利文獻1的複合測試機，即使均勻性測定結束後也 不必爲了動平衡測定而重新安裝輪胎，因此能夠縮短輪胎 裝脫所需的工時。但是，因是構成爲均勻性測定後接著進 行動平衡測定，所以必須要將輪胎的旋轉數從均勻性測定 用的低速旋轉切換成動平衡測定用的高速旋轉。然而，相 較於均勻性測定時，動平衡測定時的旋轉數是非常大，要 讓心軸增速是需要某種程度的時間。因此，上述連續進行 均勻性測定和動平衡測定的構成，對於縮短總體的試驗時 間還是有限。 本發明是有鑑於上述問題所硏創的發明，目的是提供 一種設有2個心軸藉由配合一方均勻性測定的執行對另一 方動平衡進行測定，以排列進行2個測試就能夠比先前的 複合測試機更進一步提昇測試效率的輪胎測試機及輪胎測 試方法。 [用以解決課題之手段] 爲了達成上述目的，本發明是採取下述的技術手段。 即’本發明的輪胎測試機，其特徵爲，具有：可驅動 輪胎繞著其軸心旋轉並且彼此隔著距離設置的2個心軸； -6 - 201033598 配備在上述2個心軸之間的同時設置成可對安裝在2個心 軸的各別輪胎接近離開自如的轉筒；可對與上述轉筒接觸 之一方輪胎的均勻性進行測定的均勻性測定部；及可配合 上述均勻性測定部對一方輪胎均勻性的測定，對離開上述 轉筒之另一方輪胎的動平衡進行測定的動平衡測定部。 發明人，認爲只要設有2個輪胎保持用的心軸同時使 轉筒來回2個輪胎間，就能夠配合與轉筒接觸之一方輪胎 φ 進行均勻性測定，對離開轉筒之另一方輪胎的動平衡進行 測定。 於是，發明人就得知只要設有：可對一方輪胎均勻性 進行測定的均勻性測定部；及可配合一方輪胎的均勻性測 定對另一方輪胎的動平衡進行測定的動平衡測定部，就能 夠有效率進行均勻性測定和動平衡測定，以致於完成本發 明。 另，以具有能夠以分別不同的旋轉數使安裝在上述2 φ 個心軸的輪胎旋轉的控制部爲佳。 另一方面，本發明輪胎測試方法是一種使用上述輪胎 測試機同時對安裝在一方心軸之輪胎的均句性和安裝在另 一方心軸之輪胎的動平衡進行測定的輪胎測試方法，其特 徵爲，以X(rpm)旋轉安裝在上述一方心軸的輪胎測定上述 均勻性的同時，以可滿足下述（1)式的旋轉數Y(rpm)使安 裝在上述另一方心軸的輪胎旋轉，對產生在該另一方輪胎 的動平衡進行測定。 201033598 [數式π Υ>Μ · X(l) X: —方輪胎的旋轉頻率（rPm) Μ: —方輪胎旋轉頻率的最大測定次數 另，以可滿足下述的（2)式的旋轉數Y(rpm)使安裝在 上述另一方心軸的輪胎旋轉’對產生在上述另一方輪胎的 動平衡進行測定爲佳。 [數式2] Υ = (Μ + Ν)χΧ(2) X: —方輪胎的旋轉頻率（rpm) Μ:—方輪胎旋轉頻率的最大測定次數 Ν :自然數201033598 VI. Description of the Invention: [Technical Field] The present invention relates to a tire testing machine and a tire testing method capable of measuring the uniformity and dynamic balance of a tire by the same apparatus. [Prior Art] The inspection of the tire in the production line, the measurement of the dynamic balance of the tire and the measurement of the uniformity Φ. These tests are performed using a dynamic balance tester and a uniformity tester, using different testers. However, if it is considered that the cost of the device is reduced or the productivity (production volume) is increased, it is of course better to carry out such inspections with the same device. Thus, with the prior tire testing machine, there has been developed a technique capable of performing dynamic balance measurement and uniformity measurement of a tire with one device. For example, Patent Document 1 discloses a uniformity and dynamic balance composite tester which can measure the uniformity and dynamic balance of a tire by one device. The Φ composite tester is a uniformity tester that is modified to be able to measure dynamic balance, and has a rotating means that can be converted into a low speed and high speed to rotationally drive the tire holding mandrel. The composite tester of Patent Document 1 measures the uniformity of the tire, and is configured to rotate the tire held by the spindle at a low speed, and push the drum formed as a road surface to the tire to test the uniformity of the tire. On the other hand, when measuring the dynamic balance of the tire, the tire is configured to move the tire away from the tire to rotate the tire at a high speed, thereby measuring the dynamic balance of the tire. [Provisional Technical Document] -5-201033598 [Patent Document] [Patent Document 1] Japanese Laid-Open Patent Publication No. 2004-299673 [Draft of the Invention] [Problem to be Solved by the Invention] The composite tester of Patent Document 1 ends even if the uniformity measurement is completed. It is not necessary to re-install the tire for the dynamic balance measurement, so that the man-hour required for the tire to be removed can be shortened. However, since the uniformity measurement is performed and the action balance measurement is performed, it is necessary to switch the number of rotations of the tire from the low-speed rotation for uniformity measurement to the high-speed rotation for dynamic balance measurement. However, compared to the uniformity measurement, the number of rotations in the dynamic balance measurement is very large, and it takes a certain amount of time for the mandrel to increase. Therefore, the above-described configuration for continuously performing the uniformity measurement and the dynamic balance measurement is limited in terms of shortening the overall test time. The present invention has been made in view of the above problems, and an object of the invention is to provide a method for measuring the balance of the other side by performing the measurement of the uniformity of the two mandrels, and performing the two tests in alignment to be able to perform the two tests. The compound tester further enhances the test efficiency of the tire tester and the tire test method. [Means for Solving the Problem] In order to achieve the above object, the present invention adopts the following technical means. That is, the tire testing machine of the present invention is characterized in that it has two mandrels that can drive the tire to rotate about its axis and are spaced apart from each other; -6 - 201033598 is provided between the two mandrels At the same time, it is provided as a reel capable of being close to the individual tires mounted on the two mandrels; a uniformity measuring unit capable of measuring the uniformity of one of the tires in contact with the reel; and the uniformity measurement The measurement of the uniformity of one tire, the dynamic balance measuring unit that measures the dynamic balance of the other tire leaving the drum. The inventor believes that as long as two mandrels for tire retention are provided and the drum is moved back and forth between the two tires, it is possible to perform uniformity measurement with one of the tires φ in contact with the drum, and to measure the other tire leaving the drum. The dynamic balance is measured. Then, the inventors have found that a uniformity measuring unit that can measure the uniformity of one tire and a dynamic balance measuring unit that can measure the dynamic balance of the other tire can be measured by matching the uniformity of one tire. The uniformity measurement and the dynamic balance measurement can be performed efficiently so as to complete the present invention. Further, it is preferable to have a control unit that can rotate the tires attached to the 2 φ mandrels with different numbers of rotations. On the other hand, the tire testing method of the present invention is a tire testing method for measuring the dynamic balance of the tire mounted on one of the mandrels and the dynamic balance of the tire mounted on the other mandrel using the above tire testing machine. In order to measure the uniformity by rotating the tire attached to the one mandrel at X (rpm), the tire attached to the other mandrel is rotated by the number of rotations Y (rpm) satisfying the following formula (1). The dynamic balance generated on the other tire is measured. 201033598 [Expression π Υ> Μ · X(l) X: — Rotational frequency (rPm) of the square tire Μ: — Maximum number of rotations of the square tire rotation frequency, in addition, the number of rotations satisfying the following formula (2) It is preferable that Y (rpm) rotates the tire attached to the other mandrel to measure the dynamic balance generated in the other tire. [Expression 2] Υ = (Μ + Ν) χΧ (2) X: — Rotational frequency (rpm) of the square tire Μ:—Maximum number of rotations of the square tire rotation frequency Ν : Natural number
此外，也可使上述一方輪胎的旋轉頻率X爲60(rpm) ，將旋轉頻率的最大測定次數Μ爲10次，對上述輪胎的 均勻性及動平衡進行測定。 [發明效果] 根據本發明的輪胎測試機及輪胎測試方法時，只要設 有2個心軸藉由配合一方均勻性測定的執行對另一方動平 衡進行測定，以排列進行2個測試就能夠比先前的複合測 試機更進一步提昇測試效率。 -8- 201033598 【實施方式】 [發明之最佳實施形態] 以下，根據圖面說明本發明的輪胎測試機1。 如第1圖模式所示，本實施形態的輪胎測試機1是一 種對輪胎T的均勻性（輪胎τ的均一性）和輪胎T的動平衡 (動性平衡）進行測定的複合測試裝置。輪胎測試機1是在 龜 左右隔著距離具備有2個可驅動輪胎T繞著垂直方向軸線Further, the rotation frequency X of the above-described one tire may be 60 (rpm), and the maximum number of rotations of the rotation frequency may be reduced to 10 times, and the uniformity and dynamic balance of the tire may be measured. [Effect of the Invention] According to the tire testing machine and the tire testing method of the present invention, if two mandrels are provided, the other balance can be measured by performing the measurement of the uniformity measurement, and the two tests can be performed in an array. Previous composite testers further improved test efficiency. -8 - 201033598 [Embodiment] BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a tire testing machine 1 of the present invention will be described with reference to the drawings. As shown in Fig. 1, the tire testing machine 1 of the present embodiment is a composite test device for measuring the uniformity of the tire T (the uniformity of the tire τ) and the dynamic balance (dynamic balance) of the tire T. The tire testing machine 1 has two driveable tires T around the vertical axis at a distance from the left and right sides of the turtle.
W 旋轉的心軸3。2個心軸3是旋轉自如地支撐在各自心軸 殼6，構成能夠以各別不同的旋轉數驅動旋轉輪胎T。接 著，在該等2個心軸3之間，設有可對各輪胎τ接近離開 自如的轉筒4。 以下說明中’第1圖的紙面左右是指在說明輪胎測試 機1時的左右。此外’第1圖的紙面上下是指在說明輪胎 測試機1時的上下。該等方向是和操作員如第1圖所示看 Φ 到輪胎測試機1時的方向一致。 心軸3是在轉筒4的左方設有左側的心軸3，另外在 轉筒4的右方設有右側的心軸3。該等心軸3是繞著朝向 垂直方向的軸線形成圓筒狀，其上部設有安裝輪胎用的輪 圈5。 另，2個心軸3及2個心軸殻6是除了配置爲左右對 稱以外，其他是形成相同的構成。於是，以下的說明中， 就以左側的心軸3爲代表進行說明。 心軸3的外圍側是在上端側和下端側設有2個軸承部 -9 - 201033598 (省略圖示），該軸承部使心軸3對心軸殼6成相對旋轉自 如被支撐著。心軸3的下端側具備有同步皮帶輪8，透過 圈繞在該同步皮帶輪8的同步皮帶9使心軸3能夠繞著朝 向垂直方向的軸線旋轉。 心軸殻6是形成可將心軸3收容在內側的圓筒狀，以 心軸3能夠旋轉的狀態支撐著心軸3。心軸殼6的外圍面 形成有將心軸殻6固定在底座1 〇的心軸殼支撐構件1 1， 該心軸殻支撐構件11是形成爲朝著垂直方向及左右方向 雙方延伸的板狀。 從心軸殼支撐構件11往左右方向離開的位置，配備 有從底座10朝上方突出的肋條狀定位構件12。定位構件 1 2的上端側，具備有從心軸殼支撐構件1 1往轉筒4側隔 著距離的同時和心軸殻支撐構件11成相向的相向面13， 該相向面13安裝有動平衡測定部14。心軸殼支撐構件11 和定位構件12是夾著動平衡測定部14使用緊固件（省略 圖示）成爲固定狀態，心軸殼6是使用該緊固件使心軸殼6 ^ 固定（剛體支撐）在底座10。另，針對動平衡測定部14會 在下述進行說明。 底座10是一種可從下方支撐著輪胎測試機1的機座 ，該底座10的左側和右側各配設有1台可驅動同步皮帶9 旋轉的馬達15。左右的馬達15，分別圈繞有同步皮帶9， 構成爲透過各同步皮帶9能夠對左右心軸3的同步皮帶輪 8施賦驅動力。 控制部1 6是個別驅動左側的馬達1 5和右側的馬達1 5 -10- 201033598 ，構成爲能夠以不同的旋轉數旋轉左側心軸3所支撐的輪 胎T和右側心軸3所支撐的輪胎T。 轉筒4，具備：外形爲圓筒狀的筒部17;及以旋轉自 如的狀態支撐著該筒部17的筒部支撐體18。筒部17，其 外圍面是成爲輪胎T接地的路面，形成爲能夠繞著沿著上 下方向的軸部19旋轉。轉筒4的軸部19是朝上方和下方 突出著，軸部19的突出部份是旋轉自如支撐在筒部支撐 _ 體18。該筒部支撐體18針對底座10配設成可朝左右方向 移動，筒部17是形成可接近離開被設置在心軸3的輪胎 T。此外，轉筒4和筒支撐體1 8之間，設有均勻性測定用 的均勻性測定部2 0。 本發明的輪胎測試機1，其特徵爲，具有：可對與轉 筒4接觸之一方輪胎T的均句性進行測定的均勻性測定部 2〇;及可配合均勻性測定部20對一方輪胎T均勻性的測 定，對離開轉筒4之另一方輪胎T的動平衡進行測定的動 ❹ 平衡測定部1 4。 如第2圖所示，均勻性測定部20，如上述是設置在轉 筒4的筒部17和筒部支撐體18之間，對接觸著輪胎T的 筒部1 7施加在筒部支撐體1 8的力進行測定，藉此對產生 在一方輪胎T的均勻力進行測定。本實施形態的均勻性測 定部20，例如是一種可對上下方向和左右方向的2方向成 份力進行測定的負載感測器。均勻性測定部20所測定的 均勻力是送至解析部21。 動平衡測定部1 4是分別設置在左右的心軸3，形成爲 -11 - 201033598 可對分別安裝在心軸3之輪胎τ的不平衡力進行測定。動 平衡測定部1 4是以負載感測器構成’設置在心軸殼6的 心軸殻支撐構件11和定位構件12的相向面1 3之間’將 心軸殻支撐構件11施加在定位構件12的左右方向力視爲 產生在另一方輪胎τ的不平衡力進行測定。動平衡測定部 1 4所測定的不平衡力’也是和均勻力同樣送至解析部2 1 〇 解析部21是根據均勻性測定部20所測定的均勻力對 一方輪胎Τ的均勻性進行評估的同時’根據動平衡測定部 14所測定的不平衡力對另一方輪胎Τ的動平衡進行評估 。解析部21的均勻性評估是將來自於均勻性測定部20的 振動波形分成1次至高次爲止的振動成份，以各振幅對均 勻性進行評估。此外，解析部21的動平衡評估是使用來 自於動平衡測定部1 4的振動波形，以振動波形的振幅或 頻率分析結果爲依據進行評估。 其次，針對解析部21所執行的振動解析內容，即針 對使用上述輪胎測試機1的輪胎測試方法進行詳細說明。 本發明的輪胎測試方法是配合與轉筒4接觸之一方輪 胎Τ的均勻性測定，對離開轉筒4之另一方輪胎Τ的動平 衡進行測定。具體而言，利用控制部1 6，使左右的輪胎Τ 當中的一方輪胎Τ以低旋轉數旋轉進行均勻性測定的同時 使另一方的輪胎Τ以高旋轉數旋轉進行動平衡測定。 該等均勻性測定和動平衡測定，有時會因爲轉筒4的 移動時間或心軸3增減速成指定旋轉數爲止的時間等的關 -12- 201033598 係，以致在執行一方的測定時並沒有 但是，在均勻性測定和動平衡測定同 測定系的振動沿著心軸殻6或底座 測定時，有可能無法精度佳地執行均 即，均勻性測定時輪胎T的旋轉 是較小’因此均勻性測定的振動波形 波形分解成例如10次般的高次成份 ❹ 此，即使動平衡測定系的輪胎τ的旋 的輪胎T旋轉數有很大的不同，但也 的測定頻帶或基本波形的頻率而定， 振動會影響到均勻性測定系，導致均 〇 於是，本發明爲了讓動平衡測定 干擾施加在均勻性測定系，也不會影 果，於安裝在一方心軸3的輪胎T J φ 勻性測定時，使安裝在另一方心軸3 述（1)式的旋轉數Y(rpm)旋轉，藉此達 [數式3] Υ>Μ · X (1) X: —方輪胎的旋轉頻率（rpm) Μ:—方輪胎旋轉頻率的最大測 例如：如JIS D 4 2 3 3的規定所示 執行另一方的測定。 時測定時，若動平衡 1〇以干擾傳至均勻性 勻性的評估。 數相較於動平衡測定 解析就會變成將振動 後再進行解析。基於 轉數和均与性測定系 要視振動波形解析時 有時動平衡測定系的 勻性的評估精度變差 的振動成份即使成爲 響到均勻性的評估結 以X(rpm)旋轉進行均 的輪胎T以可滿足下 ^行動平衡測定。 ί次數 ，當以X = 60rpm使安 -13- 201033598 裝在一方主軸3的輪胎T旋轉，在其M=10次成份爲止的 測定頻帶測定均勻性時，只要使安裝在另一方主軸3的輪 胎T以超過Y = 600rpm的旋轉數旋轉，藉此測定產生在另 一方的輪胎T的動平衡即可。 如此一來’即使是在均勻性測定時將振動波形分解至 Μ次成份進行評估時，但因動平衡測定系的振動頻率會比 均勻性測定系的Μ次高次諧波還高，所以就能夠使均勻性 測定系的測定頻帶和動平衡測定系的干擾振動頻帶分離， 即使動平衡測定系的振動以干擾施加在均勻性測定系也不 會呈現在振動波形的解析結果。因此，來自於動平衡測定 系的干擾就會被排除，能夠精度良好執行均勻性的評估。 另，即使是以上述的方法進行輪胎Τ測試時，但對於 均勻性測定的振動波形解析例如應用如FFT(高速傅里葉 變換）般的頻率解析時，有時還是會產生解析方法原本的 誤差。 例如：通常均句性測定是採取輪胎Τ其1次旋轉量（2 7Γ ) 的振動波形，對該振動波形進行FFT解析。然而，FFT解 析爲了要達到解析目的其前提條件是解析時間內振動波形 爲週期性重覆。因此，動平衡測定的旋轉頻率若偏離均勻 性測定的旋轉頻率整數倍時，則動平衡測定系的振動波形 重疊之均勻性測定所使用的振動波形不會連接成週期性， 導致分析波形的最初和最後沒有順暢連續。對上述振動 波形進行FFT解析時，被稱爲「遺漏成份」的誤差成份（ 假的成份）會加入至高次成份，以致有可能無法精度良好 -14- 201033598 執行均勻性的評估。 於是，本發明是以可滿足下述（2)式的旋轉數Y(rpm) 旋轉安裝在另一方心軸3的輪胎T進行動平衡測定。 [數式4] Y = (M + N)xX (2) X: —方輪胎的旋轉頻率（rpm) φ Μ : —方輪胎旋轉頻率的最大測定次數 Ν :自然數 例如：如上述JIS D423 3所規定的測試條件時，當安 裝在一方心軸3的輪胎T以X = 60rpm旋轉，在其M=l〇次 成份爲止的測定頻帶進均勻性測定時，只要將安裝在另一 方心軸3的輪胎T以Y = 660rpm以上且60rpm整數倍的旋 轉數旋轉，藉此測定產生在另一方輪胎T的動平衡即可。 # 如此一來’因動平衡測定系的輪胎T的旋轉數和均勻 性測定系的輪胎T的旋轉數是成整數倍關係，所以均勻性 測定所使用的振動波形是以2 π連接成週期性，使分析波 形的最初和最後連續成順暢。因此，就不會產生如遺漏成 份般的誤差成份，能夠精度更好地執行均勻性的評估。 其次，以掲示解析部21的分析波形的解析結果來說 明本發明的輪胎測試方法。 第3圖是表示—方輪胎τ的旋轉頻率爲6〇rpm，另— 方輪胎Τ的旋轉頻率爲720rpm時，解析部21所測定之均 -15- 201033598 勻力的振動波形。 該實驗例中，對於均勻力的振動波形爲了要在最大10 次爲止的測定頻帶進行 FFT解析，將 x = 60rpm、 Y = 72 0rpm、M=10，藉此滿足（1)式及（2)式的關係。 另一方面，解析部21所測定之均句力的振動波形， 如第3圖所示，在以60 rpm的正弦波爲基本波形的1次 成份，重疊有72〇rptn的高頻。對該振動波形的最初和最 後進行比較時，可得知振動波形的最初和最後連續成順暢 ，在解析時間內振動波形爲週期性重覆。 如第4圖所示，當對該均勻力的振動波形在最大1〇 次爲止的測定頻帶進行FFT解析時，只測定出1次成份的 振動成份，並未測定出2次至1 〇次爲止的高次振動成份 。基於此，可得知若是滿足上述（1)式及（2)式的關係時， 各次成份就不會產生遺漏成份等誤差成份，能夠精度更好 地評估均勻性。 另一方面，第5圖是表示一方輪胎T的旋轉頻率爲 60rpm，另一方輪胎T的旋轉頻率爲690rpm時，解析部 21所測定之均勻力的振動波形。基於此，雖滿足上述（1) 式的關係，但並未滿足上述（2)式的關係。 此時，如第5圖所示，針對解析部21所測定之均勻 力的振動波形進行分析波形的最初和最後之比較時，可得 知振動波形的最初和最後並沒有連續成順暢，在解析時間 內振動波形沒有週期性重覆。 如第6圖所示，當對該均勻力的振動波形在最大1〇 -16- 201033598 次爲止的測定頻帶進行FFT解析時，測定出2次至1 0次 爲止的高次振動成份有遺漏成份。基於此，可判斷出沒有 滿足上述（2)式之關係的實驗例，各次數的振動成份會產生 遺漏成份等誤差成份，無法以更好的精度評估均句性° 本發明並不限於上述各實施形態，在未變更發明本質的 範圍內是可適宜變更各構件的形狀、構造、材質、組合等。 上述實施形態中，心軸3是以2軸爲例示。但是’心 _ 軸3也可設置成3軸以上。 上述實施形態中，均勻性測定部20是以設置在筒部 1 7和筒部支撐體1 8之間可測定2方向成份力的負載感測 器爲例示的同時，動平衡測定部1 4是以設置在心軸殼6 的心軸殼支撐構件Π和定位構件1 2的相向面1 3之間可 測定1方向成份力的負載感測器爲例示。但是，均勻性測 定部20或動平衡測定部14也可設置在例示位置以外的位 置。例如：均勻性測定部20也可設置在心軸殼6側。此 φ 外，對於該等測定部也可使用能夠測定3方向成份的負載 感測器或壓力感測器等。 【圖式簡單說明】 第1圖爲輪胎測試機的正面圖。 第2圖爲輪胎Τ測試時的輪胎測試機正面圖。 第3圖爲表示實施例的振動波形圖表。 第4圖爲表示實施例振動波形的FFT解析結果的圖表。 第5圖爲比較例振動波形的圖表。 -17- 201033598 第6圖爲比較例振動波形的FFT解析結果的圖表。 【主要元件符號說明】 1 :輪胎測試機 3 :心軸 4 :轉筒 5 :輪圈 6 :心軸殼 _ 7 :軸承部 8 :同步皮帶輪 9 :同步皮帶 10 :底座 1 1 :心軸殼支撐構件 1 2 :定位構件 1 3 :相向面 1 4 :動平衡測定部 _ 1 5 :馬達 1 6 :控制部 1 7 :筒部 18 :筒支撐體 19 :軸部 20 :均勻性測定部 2 1 :解析部 T :輪胎 -18-W Rotating mandrel 3. The two mandrels 3 are rotatably supported by the respective mandrel shells 6, and are configured to be capable of driving the rotating tire T with different numbers of rotations. Next, between the two mandrels 3, there is provided a drum 4 which is capable of approaching and leaving each of the tires τ. In the following description, the left and right sides of the paper in the first drawing are the left and right when the tire testing machine 1 is explained. Further, the upper and lower sides of the paper in Fig. 1 refer to the upper and lower sides when the tire testing machine 1 is explained. These directions are the same as the direction in which the operator sees Φ to the tire testing machine 1 as shown in Fig. 1. The mandrel 3 is provided with a left side mandrel 3 on the left side of the drum 4, and a right side mandrel 3 on the right side of the drum 4. The mandrels 3 are formed in a cylindrical shape about an axis oriented in the vertical direction, and a rim 5 for mounting a tire is provided on the upper portion thereof. Further, the two mandrels 3 and the two mandrel shells 6 have the same configuration except that they are arranged to be symmetrical. Therefore, in the following description, the mandrel 3 on the left side will be described as a representative. On the outer peripheral side of the mandrel 3, two bearing portions -9 - 201033598 (not shown) are provided on the upper end side and the lower end side, and the bearing portion allows the mandrel 3 to be relatively rotatably supported by the mandrel housing 6. The lower end side of the mandrel 3 is provided with a timing pulley 8, and the timing belt 9 wound around the timing pulley 8 allows the spindle 3 to rotate about an axis directed in the vertical direction. The mandrel shell 6 is formed in a cylindrical shape in which the mandrel 3 can be accommodated inside, and the mandrel 3 is supported in a state in which the mandrel 3 is rotatable. The outer peripheral surface of the mandrel shell 6 is formed with a mandrel shell supporting member 1 1 for fixing the mandrel shell 6 to the base 1 , and the mandrel shell supporting member 11 is formed in a plate shape extending in both the vertical direction and the left and right direction. . A rib-like positioning member 12 projecting upward from the base 10 is provided at a position away from the mandrel shell support member 11 in the left-right direction. The upper end side of the positioning member 1 2 is provided with a facing surface 13 that faces the mandrel shell supporting member 11 while being spaced from the mandrel shell supporting member 1 1 toward the drum 4 side, and the opposing surface 13 is mounted with a dynamic balance. Measurement unit 14. The mandrel shell support member 11 and the positioning member 12 are fixed to each other with a fastener (not shown) interposed therebetween, and the mandrel shell 6 is fixed by the fastener (6) (the rigid body support) At the base 10. The dynamic balance measuring unit 14 will be described below. The base 10 is a base that supports the tire testing machine 1 from below, and a motor 15 for driving the timing belt 9 to rotate is disposed on the left and right sides of the base 10. The right and left motors 15 are wound around the timing belts 9, respectively, and are configured to be capable of imparting a driving force to the timing pulleys 8 of the left and right spindles 3 through the timing belts 9. The control unit 16 is a motor 15 on the left side and a motor 1 5 -10- 201033598 on the right side, and is configured to be able to rotate the tire T supported by the left mandrel 3 and the tire supported by the right mandrel 3 with different numbers of rotations. T. The drum 4 includes a cylindrical portion 17 having a cylindrical outer shape, and a tubular support 18 that supports the tubular portion 17 in a rotatable state. The cylindrical portion 17 has a peripheral surface which is a road surface on which the tire T is grounded, and is formed to be rotatable about the shaft portion 19 in the up-and-down direction. The shaft portion 19 of the drum 4 is protruded upward and downward, and the protruding portion of the shaft portion 19 is rotatably supported by the tubular support body 18. The tubular support body 18 is disposed to be movable in the left-right direction with respect to the base 10, and the tubular portion 17 is formed to be accessible from the tire T provided on the mandrel 3. Further, a uniformity measuring unit 20 for uniformity measurement is provided between the drum 4 and the cylinder support body 18. The tire testing machine 1 of the present invention is characterized in that it has a uniformity measuring unit 2 that can measure the uniformity of the one-side tire T in contact with the drum 4, and a uniformity measuring unit 20 can be used to match one tire. The measurement of the T uniformity is a dynamic balance measuring unit 14 that measures the dynamic balance of the other tire T leaving the drum 4. As shown in Fig. 2, the uniformity measuring unit 20 is provided between the tubular portion 17 of the drum 4 and the tubular portion support 18 as described above, and is applied to the tubular portion of the tubular portion 17 that is in contact with the tire T. The force of 18 was measured, and the uniform force generated in one tire T was measured. The uniformity measuring unit 20 of the present embodiment is, for example, a load sensor that can measure the force in two directions in the vertical direction and the horizontal direction. The uniform force measured by the uniformity measuring unit 20 is sent to the analyzing unit 21. The dynamic balance measuring unit 14 is provided on the right and left mandrels 3, and is formed as -11 - 201033598 to measure the unbalanced force of the tires τ attached to the mandrels 3, respectively. The dynamic balance measuring portion 14 is constituted by a load sensor 'between the facing shell support member 11 of the mandrel shell 6 and the facing surface 13 of the positioning member 12'. The mandrel shell supporting member 11 is applied to the positioning member 12 The left-right direction force is measured as an imbalance force generated in the other tire τ. The unbalanced force ' measured by the dynamic balance measuring unit 14 is also sent to the analyzing unit 2 in the same manner as the uniform force. The analyzing unit 21 evaluates the uniformity of one of the tire dams based on the uniform force measured by the uniformity measuring unit 20. At the same time, the dynamic balance of the other tire raft is evaluated based on the imbalance force measured by the dynamic balance measuring unit 14. The uniformity of the analysis unit 21 is obtained by dividing the vibration waveform from the uniformity measuring unit 20 into a high-order vibration component, and evaluating the uniformity of each amplitude. Further, the dynamic balance evaluation by the analysis unit 21 is performed using the vibration waveform from the dynamic balance measuring unit 14 and based on the amplitude or frequency analysis result of the vibration waveform. Next, the vibration analysis content executed by the analysis unit 21, that is, the tire test method using the tire tester 1 described above will be described in detail. The tire testing method of the present invention measures the uniformity of one of the tire tires that are in contact with the drum 4, and measures the dynamic balance of the other tire rim leaving the drum 4. Specifically, the control unit 16 causes one of the left and right tires 旋转 to rotate with a low number of rotations to measure the uniformity, and the other tire Τ to perform the dynamic balance measurement with a high number of rotations. The uniformity measurement and the dynamic balance measurement may be caused by the movement time of the drum 4 or the time when the mandrel 3 is increased or decreased to a predetermined number of rotations, etc., so that one of the measurements is performed. However, when the uniformity measurement and the dynamic balance measurement are measured along the spindle housing 6 or the base, the vibration of the tire T may be performed with less precision. The waveform of the vibration waveform measured by the uniformity is decomposed into a high-order component such as 10 times. Therefore, even if the number of rotations of the tire T of the tire τ of the dynamic balance measurement system is greatly different, the measurement band or the basic waveform is also used. Depending on the frequency, the vibration affects the uniformity measurement system, resulting in uniformity. In order to make the dynamic balance measurement interference applied to the uniformity measurement system, the present invention does not affect the tire TJ φ mounted on one of the mandrels 3. In the measurement of the uniformity, the number of rotations Y (rpm) of the equation (1) attached to the other mandrel 3 is rotated, thereby reaching [Expression 3] Υ > Μ · X (1) X: - rotation of the square tire Frequency (rpm) Μ: - square tire The maximum transfer frequency measurement example: As shown in JIS D 4233 a predetermined measurement execution of the other. When measuring, if the dynamic balance is 1 〇 to interfere with the assessment of the uniformity of uniformity. The number is compared to the dynamic balance measurement. The analysis becomes the vibration and then the analysis. In the case of the calculation of the vibration waveform, the vibration component of the uniformity of the dynamic balance measurement system may be deteriorated even if the evaluation result of the uniformity is X (rpm) rotation. The tire T is measured to meet the balance of the action. For the number of times, when the tire T mounted on one of the main shafts 3 is rotated at X = 60 rpm, and the uniformity is measured in the measurement band of the M = 10 components, the tire attached to the other main shaft 3 is used. T is rotated by a number of revolutions exceeding Y = 600 rpm, whereby the dynamic balance generated in the other tire T can be measured. In this way, even when the vibration waveform is decomposed into the fractional component for evaluation during the uniformity measurement, the vibration frequency of the dynamic balance measurement system is higher than the higher harmonic of the uniformity measurement system, so The measurement frequency band of the uniformity measurement system and the interference vibration frequency band of the dynamic balance measurement system can be separated, and even if the vibration of the dynamic balance measurement system is applied to the uniformity measurement system by interference, the analysis result of the vibration waveform does not appear. Therefore, interference from the dynamic balance measurement system is eliminated, and the uniformity can be evaluated with high precision. In addition, even when the tire flaw test is performed by the above method, when the vibration waveform analysis for the uniformity measurement is applied, for example, when frequency analysis such as FFT (fast Fourier transform) is applied, the original error of the analysis method may occur. . For example, in general, the uniformity measurement is a vibration waveform in which the tire is rotated once (2 7 Γ), and the vibration waveform is subjected to FFT analysis. However, the premise of the FFT analysis for the purpose of analysis is that the vibration waveform is periodically repeated during the analysis time. Therefore, if the rotational frequency of the dynamic balance measurement deviates from the integral frequency of the rotation frequency of the uniformity measurement, the vibration waveform used for the measurement of the uniformity of the vibration waveform overlap of the dynamic balance measurement system is not connected to the periodicity, resulting in the initial analysis waveform. And the last is not smooth and continuous. When FFT analysis is performed on the above vibration waveform, the error component (false component) called "missing component" is added to the high-order component, so that it may not be accurate -14- 201033598 Performing the uniformity evaluation. Then, the present invention performs dynamic balance measurement by rotating the tire T attached to the other mandrel 3 at a number of revolutions Y (rpm) satisfying the following formula (2). [Expression 4] Y = (M + N)xX (2) X: - Rotational frequency (rpm) of the square tire φ Μ : - Maximum number of measurements of the square tire rotation frequency Ν : Natural number: For example, JIS D423 3 above In the case of the specified test conditions, when the tire T attached to one of the mandrels 3 is rotated at X = 60 rpm, and the measurement band of the M = 1 成份 component is measured for uniformity, it is to be mounted on the other mandrel 3 The tire T is rotated at a number of revolutions of Y = 660 rpm or more and an integral multiple of 60 rpm, whereby the dynamic balance generated in the other tire T can be measured. # As a result, the number of revolutions of the tire T and the number of revolutions of the tire T in the uniformity measurement system are integer multiples, so the vibration waveform used for the uniformity measurement is connected by periodicity of 2 π. , so that the initial and final continuation of the analysis waveform is smooth. Therefore, an error component such as a missing component is not generated, and the uniformity evaluation can be performed with higher precision. Next, the tire test method of the present invention will be described with reference to the analysis result of the analysis waveform of the analysis unit 21. Fig. 3 is a view showing a vibration waveform of a uniform force of -15 - 201033598 measured by the analyzing unit 21 when the rotation frequency of the square tire τ is 6 rpm and the rotation frequency of the other tire Τ is 720 rpm. In this experimental example, the FFT analysis is performed on the measurement waveform of the maximum force for the vibration waveform of the uniform force, and x (60), Y = 72 0 rpm, and M = 10, thereby satisfying the formula (1) and (2). Relationship. On the other hand, as shown in Fig. 3, the vibration waveform of the average sentence force measured by the analyzing unit 21 has a high frequency of 72 〇rptn superimposed on the primary component having a sine wave of 60 rpm as a basic waveform. When the initial and final comparisons of the vibration waveform are made, it is known that the first and last continuous smoothness of the vibration waveform is smooth, and the vibration waveform is periodically repeated during the analysis time. As shown in Fig. 4, when the FFT analysis is performed on the measurement band of the uniform force vibration waveform at the maximum of 1 time, only the vibration component of the primary component is measured, and the measurement is not performed twice to 1 time. High-order vibration components. Based on this, it can be seen that if the relationship between the above formulas (1) and (2) is satisfied, the error components such as missing components are not generated for each component, and the uniformity can be evaluated with higher accuracy. On the other hand, Fig. 5 is a vibration waveform showing the uniform force measured by the analyzing unit 21 when the rotational frequency of one tire T is 60 rpm and the rotational frequency of the other tire T is 690 rpm. Based on this, although the relationship of the above formula (1) is satisfied, the relationship of the above formula (2) is not satisfied. At this time, as shown in FIG. 5, when the first and last comparisons of the analysis waveforms are performed on the vibration waveform of the uniform force measured by the analysis unit 21, it is understood that the first and the last of the vibration waveform are not continuously smooth, and the analysis is performed. The vibration waveform does not repeat periodically during the time. As shown in Fig. 6, when the FFT analysis is performed on the measurement band of the uniform force vibration waveform from the maximum of 1〇-16 to 201033598 times, the high-order vibration component from the second to the tenth time is measured as a missing component. . Based on this, it can be judged that the experimental example in which the relationship of the above formula (2) is not satisfied, the vibration components of the respective times generate error components such as missing components, and the uniformity cannot be evaluated with better precision. The present invention is not limited to the above. In the embodiment, the shape, structure, material, combination, and the like of each member can be appropriately changed within the range in which the essence of the invention is not changed. In the above embodiment, the mandrel 3 is exemplified by two axes. However, the 'heart' axis 3 can also be set to be three or more axes. In the above-described embodiment, the uniformity measuring unit 20 is exemplified by a load sensor that can measure the two-direction component force between the tubular portion 17 and the tubular portion support 18, and the dynamic balance measuring unit 14 is A load sensor capable of measuring a one-direction component force between the mandrel case supporting member 心 of the mandrel case 6 and the facing surface 13 of the positioning member 12 is exemplified. However, the uniformity measuring unit 20 or the dynamic balance measuring unit 14 may be provided at a position other than the exemplary position. For example, the uniformity measuring unit 20 may be provided on the mandrel shell 6 side. In addition to this φ, a load sensor, a pressure sensor, or the like capable of measuring a three-direction component can be used for the measurement unit. [Simple description of the drawing] Figure 1 is a front view of the tire testing machine. Figure 2 is a front view of the tire testing machine during tire tread testing. Fig. 3 is a graph showing a vibration waveform of the embodiment. Fig. 4 is a graph showing the results of FFT analysis of the vibration waveform of the embodiment. Fig. 5 is a graph showing the vibration waveform of the comparative example. -17- 201033598 Fig. 6 is a graph showing the results of FFT analysis of the vibration waveform of the comparative example. [Main component symbol description] 1 : Tire tester 3 : Mandrel 4 : Drum 5 : Rim 6 : Mandrel housing _ 7 : Bearing part 8 : Timing pulley 9 : Timing belt 10 : Base 1 1 : Mandrel housing Support member 1 2 : positioning member 1 3 : opposing surface 1 4 : dynamic balance measuring unit _ 1 5 : motor 1 6 : control unit 1 7 : cylindrical portion 18 : cylindrical support 19 : shaft portion 20 : uniformity measuring portion 2 1 : Analysis Department T: Tire-18-